JPH10226244A - Hub clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent arms of a retainer for holding a sliding gear from being deformed. SOLUTION: The hub clutch is provided with a housing fixed to the wheel side, a drive gear fixed to the driving shaft, a sliding gear connected to the housing and movable to a connecting position and a disconnecting position at which the sliding gear is to be connected to and disconnected from the drive gear, a retainer 1 which inserts an insertion part 11 for plural arms 7 formed on a flange part 5 through a base part 9 into an engaging groove 17, and which locks the gear by means of claws 13 formed on the tip of the respective arms 7 and bent inwardly, and a control means for controlling the gear to be moved to the connecting position through the retainer 1. Further, between the insertion part 11 and the engaging groove 17, a gap 22 is formed on the tip side of the insertion part 11 while the contact area 21 remains on the base part 9 side of the arm 7, and the contact place between the insertion part 11 and the engaging groove 17 is allowed to move to the base part 9 side.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hub clutch for connecting and disconnecting between a drive axle and wheels in a four-wheel drive vehicle.

[0002]

2. Description of the Related Art A hub clutch 201 as shown in FIG. 8 is described in Japanese Patent Application Laid-Open No. 1-215629.

In the following description of the hub clutch 201, the left and right directions correspond to FIG. 8 and the left and right directions of the vehicle, and members and the like without reference numerals are not shown.

[0004] A housing 203 of the hub clutch 201 is fixed to a wheel hub of the right wheel by bolts 205. A drive gear 2 is provided at the right end of the drive shaft 207.
09 is spline-connected.

[0005] A slide gear 213 meshes with a spline 211 provided on the inner periphery of the housing 203 via an outer spline 215 and is connected to be movable in the axial direction. The slide gear 213 is movable to a connection position where the slide gear 213 is engaged with the drive gear 209 to connect the housing 203 and the drive gear 209, and a disengagement position in FIG. 8 where the engagement is released.

[0008] As shown in FIGS. 8 to 11, a retainer 217 is shown.
Is formed from a flange portion 219 and two arms 221. Each arm 221 has a base 223 on the flange 219 side.
And an insertion portion 225 provided on the distal end side of the base portion 223, and the tip of the insertion portion 225 has an inwardly bent claw 22.
7 are provided.

The insertion portion 225 of each arm 221 has a toothless portion 229 formed on a spline 215 of the slide gear 213.
(Engagement groove).

The retainer 217 has a flange portion 219 and a claw 2
27, the slide gear 213 is held movably in the axial direction. A shift spring 231 is provided between the flange 219 of the retainer 217 and the slide gear 213.
Are arranged, and the slide gear 213 is connected to the drive gear 209.
To the engagement side (connection position).

A spline 235 is provided on the outer periphery of the boss 233 of the drive gear 209, and a ring member 237 meshes with the spline 235 so as to be movable in the axial direction. The flange portion 219 of the retainer 217 is fixed to the ring member 237.

A return spring 239 is arranged between the ring member 237 and the drive gear 209, and
The slide gear 213 is pressed to the side where the engagement with the drive gear 209 is released (the side where the connection is released) via the screw 217.

On the left side of the retainer 217, a cam member 241 having a V-shaped groove-like cam portion is disposed.
35 is movably connected in the axial direction.

An outer brake is provided on the spindle on the vehicle body side.
The key 243 is non-rotatably connected. Outer brake
A V-shaped groove-shaped cam portion that engages with the cam portion of the cam member 241 is provided at the right end of the key 243.

An inner brake 245 is disposed on the inner peripheral side of the outer brake 243 so as to be relatively rotatable. At the right end of the inner brake 245, a V-shaped first cam portion engaging with the cam portion of the cam member 241 is provided, and second cam portions are provided on both sides in the rotation direction. .

Outer brake 243 and inner brake
A wire brake 247 is arranged between the key 245 and the key 245. The wire brake 247 is formed in a C-shape, and has bent portions 249 that are bent inward at both ends.

A release plate 251 is fixed to the outer periphery of the boss 233 of the drive gear 209. The release plate 251 abuts against the bent portion 249 of the wire brake 247 from the outside in the circumferential direction. An arm 253 is formed. The inner brake 245 is formed with a projection that abuts the bent portion 249 from the inside in the circumferential direction.

[0016] Outer brake 243 and inner brake
The keys 245 are locked together to form a unit.

A washer 254 and a thrust bearing 255 are disposed between the outer brake 243 and the inner brake 245, and receive the cam force of each of the cams.

Thus, a cam mechanism 257 (operating means) for moving the slide gear 213 is constituted.

A bearing 259 is disposed between the right end of the drive gear 209 and the housing 203. The bearing 259 is provided by centering the housing 203 and the drive gear 209 to form the slide gear 213. The engagement with the drive gear 209 is facilitated.

The hub clutch 201 is assembled by mounting a retainer 217 and a slide gear 21 inside the housing 203.
3, a shift spring 231, a drive gear 209, a return spring 239, a cam member 241, a release plate 251 and the like are incorporated.
43, wire brake 247, and inner brake 24
5 is incorporated as a unit.

The housing 203 in which all the members are assembled is mounted on the drive shaft 207 side and the spindle side while the drive gear 209 is spline-connected to the drive shaft 207.

Prior to this assembly, the shift spring 231 and the slide gear 213 are assembled to the retainer 217.

When the vehicle is switched from the two-wheel drive state to the four-wheel drive state, when the driving force of the engine is transmitted to the drive shaft 207, the cam member 241 rotates integrally with the drive gear 209, and the outer shake on the spindle side is performed. -Ki 24
3 moves to the right due to the cam thrust force generated between them. The inner brake 245 rotates together with the cam member 241 while meshing with the cam member 241.

Next, with the rotation of the inner brake 245, the projection of the inner brake 245 is bent.
, The wire brake 247 is pushed and spread to generate a brake torque between the wire brake 247 and the outer brake 243. This brake torque causes the inner brake 2
45 is fixed to the outer brake 243.

When the inner brake 245 is fixed,
The cam member 241 climbs over the first cam portion of the inner brake 245, further rides on the second cam portion, and moves rightward along the second cam portion.

The rightward movement of the cam member 241 causes the return spring 239 to be bent, and the slide gear 213 via the retainer 217 and the shift spring 231.
Is pressed rightward.

At this time, as described above, the slide gear 2
Until the phases of the drive gear 13 and the drive gear 209 match, ratcheting occurs due to the relative rotation. However, the shift spring 231 presses the slide gear 213 toward the drive gear 209, and when the phases match, the shift gear 213 is moved. Bite. Slide gear 213 and drive gear 209
The vehicle is brought into a four-wheel drive state by meshing with.

The slide gear 213 is connected to the drive gear 2.
After the engagement with the drive gear 209, the arm 253 of the release plate 251 rotating together with the drive gear 209 collides with the bent portion 249 of the wire brake 247 from the outside to eliminate the brake torque.

When changing from the four-wheel drive state to the two-wheel drive state, the vehicle is moved slightly in the direction opposite to the current traveling direction after the drive shaft 207 is separated from the engine side.
The return spring 239 causes the cam portion of the cam member 241 to move to the left along the second cam portion of the inner brake 245, and finally the cam portion of the outer brake 243 and the inner brake. 245 with the first cam portion.
In the course of the cam member 241 moving to the left in this manner, the engagement between the slide gear 213 and the drive gear 209 is released, and the vehicle enters a two-wheel drive state.

[0030]

When switching to the four-wheel drive state, if the slide gear 213 engages with the drive gear 209, no torque is applied to the retainer 217, but the slide gear 213 and the drive gear 209 are connected to each other. If the phases do not match, as described above, they rotate relative to each other, and ratcheting occurs.

As shown in FIG. 11, the impact force 261 at this time is
May be caught on the arm 221 of the retainer 217, and in some cases, a crack 263 may enter the base 223 and deform the arm 221.

To prevent deformation of the arm 221, for example,
It is necessary to take measures such as increasing the thickness of the entire retainer 217 or the thickness of the arm 221. However, the cost of the retainer 217 increases and the weight increases, which is disadvantageous.

Accordingly, an object of the present invention is to provide a hub clutch in which a retainer for holding a slide gear does not deform even when a torque is applied.

[0034]

According to a first aspect of the present invention, there is provided a hub clutch, comprising: a housing fixed to a wheel hub on a wheel side;
A drive gear fixed to the drive shaft, a slide gear meshing with a spline on the inner circumference of the housing with a spline on the outer periphery, and a slide gear movable to a coupling position meshing with the drive gear and a disengagement position where the meshing is released, and a base. A plurality of arms formed in the flange portion are inserted into engagement grooves provided on the outer periphery of the slide gear, and the slide gear is locked by claws formed at the ends of the arms and bent inward. And an operating means for moving the slide gear to the connection position via a retainer, and between the insertion portion and the engagement groove, the contact portion being opposite to the base while leaving a contact portion on the base side of the arm. By forming a gap on the side, the contact point between the insertion portion and the engagement groove is moved to the base side.

Thus, in the hub clutch according to the first aspect, between the insertion portion of the retainer and the engagement groove of the slide gear, the contact portion is provided at the base side of the insertion portion while the contact portion is provided on the opposite side (the arm). A contact point between the insertion portion and the engagement groove was moved to the base side by forming a gap at the front end side of the base.

The moment applied to the base of the retainer becomes smaller due to the movement of the contact portion with the engagement groove of the slide gear toward the base, so that the moment until the phase of the slide gear matches the phase of the drive gear. The force applied to the base of the arm at the time of checking is greatly reduced as compared with the conventional example, cracking and deformation of the retainer are prevented, and the function of the hub clutch can be normally maintained for a long time.

Therefore, it is not necessary to take measures such as making the retainer thicker, and it is possible to avoid cost increase and weight increase.

According to a second aspect of the present invention, in the hub clutch according to the first aspect, in the engagement groove of the slide gear, the base side of the spline teeth on both sides is made thicker, or a notch is formed on the opposite side of the base. Characterized in that the contact point between the insertion portion and the engagement groove is moved to the base side by providing
An effect equivalent to that of the configuration of claim 1 is obtained.

In addition, the spline teeth are made thicker or notches are provided on the slide gear side in order to move the contact portion to the base side, so that the retainer does not need to be changed. The accompanying increase in the cost of the retainer can be avoided.

In a configuration in which the spline teeth are made thicker to move the contact point, the spline is advantageously strengthened accordingly.

According to a third aspect of the present invention, there is provided the hub clutch according to the first aspect, wherein a notch parallel to the insertion direction is provided at both side edges of the insertion portion so that the contact portion between the insertion portion and the engagement groove is provided. Is moved to the base side, and the same effect as the configuration of claim 1 is obtained.

In addition, a notch is provided on the insertion portion side of the retainer in order to move the contact point to the base side, so that the slide gear does not need to be changed, and the cost of the slide gear increases with the change. Can be avoided.

Also, since there is a claw at the tip of the arm, when assembling the slide gear to the retainer, the slide gear is moved to the inside of the retainer with the arm largely bent outward so that the claw does not hit. And the arm is inserted through the engagement groove of the slide gear. However, conventionally, the arm may be deformed when the arm is largely bent outward as described above, and the assembling work is also difficult.

However, in the structure of the third aspect, the width of the insertion portion becomes narrower than that of the base portion by providing the notch on the edge portion, and the flexibility is greatly improved, so that the claw does not hit the slide gear. Even if the insertion portion (arm) is greatly bent, there is no possibility that the arm is deformed, the assembly is facilitated, and the workability is improved.

Further, even if the width of the insertion portion is reduced, the width of the base is not changed, so that the strength of the arm does not decrease.

According to a fourth aspect of the present invention, there is provided the hub clutch according to the first aspect, wherein the insertion portion and the engagement groove are formed by providing cutouts which become wider toward the distal end on both sides of the insertion portion. The contact point has been moved to the base side,
An effect equivalent to that of the configuration of claim 1 is obtained.

In addition to the above, equivalent to the structure of the third aspect,
Since the notch is provided on the insertion portion side of the retainer, it is not necessary to change the slide gear, and since the notch is provided on the edge, the flexibility of the insertion portion is greatly improved. Therefore, the insertion portion (arm) is not likely to be deformed even if it is greatly deformed during assembly, and assembling is easy and workability is improved.

[0048]

1 to 3 show a first embodiment of the present invention.
An embodiment will be described. FIG. 1 shows a retainer 1 and a slide gear 3 used in the hub clutch of this embodiment, and this embodiment has the features of claims 1 and 2.

In this embodiment, the retainer 1
The members other than the slide gear 3 and the slide gear 3 are the same as those in the conventional example of FIG. 8, and the functions of the retainer 1 and the slide gear 3 with respect to other members are the same as those of the conventional retainer 217 and slide gear 213. Therefore, in the following description, the same reference numerals are given to the same functional members as in the conventional example, and the same functional members are referred to, and redundant description of these same functional members is omitted.

As shown in each of the drawings, the retainer 1 has a flange 5
And two arms 7 provided at equal intervals to each other. Each arm 7 includes a base 9 on the flange portion 5 side and an insertion portion 11 on the distal end side of the base 9, and a claw 13 bent inward is provided at the distal end of each insertion portion 11. Each arm 7
Is inserted through a toothless portion 17 (engaging groove) formed in a spline 15 provided on the outer periphery of the slide gear 3.

As shown in FIGS. 2 and 3, the slide gear 3
The toothless portion 17 has a thick portion 19 having a large tooth thickness on the base 9 side of the spline teeth on both sides to form a contact portion 2 with the insertion portion 11.
1 was formed, and the thick portion 19 was formed on the base 9 side, so that the gap 22 was formed on the claw 14 side of the insertion portion 11.

As described above, by forming the gap 22 on the claw 14 side, the contact portion (contact portion 21) between the insertion portion 11 and the toothless portion 17 is moved to the base 9 side.

The slide gear 3 is formed by forging. Further, the toothless portion 17 and the thick portion 19 may be cut.

Thus, the hub clutch of the first embodiment is configured.

Arrow 23 in FIG. 3 indicates the position of the force applied to the base 9 of the arm 7 during ratcheting until the phase is matched when the slide gear 3 meshes with the drive gear 209, and arrow 261 indicates the position in FIG. The position of the force applied to the base 9 is shown in the configuration of the conventional example as described above.

At the time of ratcheting, the base 9 of the retainer 1
In the moment, the contact point between the arm 7 and the toothless portion 17 becomes smaller by the distance moved to the base 9 side as compared with the conventional example, so that the force applied to the base 9 is reduced accordingly, and cracks and Deformation is prevented, and the function of the hub clutch is kept normal for a long time.

Therefore, it is not necessary to take measures such as increasing the thickness of the retainer 1, thereby avoiding an increase in cost and weight.

Further, since the thickened portion 19 is formed in the toothless portion 17 of the slide gear 3 in order to move the contact portion, the retainer 1 does not need to be changed, and the cost increase due to the change is avoided. Can be

Further, since the tooth thickness is increased by the thick portion 19, the spline 15 is advantageously strengthened accordingly.

In order to move the contact portion to the base 9 side, a cutout may be provided at the tip end side of the insertion portion 11 in the spline teeth on both sides of the toothless portion 17.

Next, a second embodiment of the present invention will be described with reference to FIGS. Each of the drawings shows a retainer 25 and a slide gear 213 used in the hub clutch of this embodiment, and this embodiment has the features of claims 1 and 3. The slide gear 213 is the same as that used in the conventional example of FIG.

As shown in the figures, the retainer 25 is formed by a flange portion 27 and two arms 29 provided at equal intervals from each other. Each arm 29 has a base 3 on the flange 27 side.
1 and an insertion portion 33 on the distal end side of the base portion 31, and a claw 35 bent inward is provided at the distal end of each insertion portion 33. The insertion portion 33 of each arm 29 is inserted into a toothless portion 229 provided on a spline 215 of the slide gear 213.

As shown in FIG. 5, the insertion portion 33 of the retainer 25 has cutouts 39 parallel to the insertion direction on both sides while leaving a contact portion 37 with the toothless portion 229 on the base 31 side. The insertion portion 33
The contact portion (contact portion 37) between the teeth 31 and the toothless portion 229 is
Has been moved to the side.

Thus, the hub clutch of the second embodiment is configured.

The arrow 41 in FIG. 5 indicates the position of the force applied to the base 31 of the arm 29 during ratcheting until the phase is matched when the slide gear 213 meshes with the drive gear 209.

The moment applied to the base 31 of the retainer 25 during ratcheting is such that the contact point between the arm 29 and the toothless portion 229 is smaller by the distance moved toward the base 31 than in the conventional example. Therefore, the force applied to the base portion 31 is reduced accordingly, cracks and deformation are prevented, and the function of the hub clutch can be normally maintained for a long time.

Accordingly, it is not necessary to take measures such as making the retainer 25 thicker, and it is possible to avoid cost increase and weight increase.

Further, since the notch 39 is provided on the retainer 25 side in order to move the contact portion to the base 31 side, the slide gear 213 does not need to be changed, and the cost increase due to the change can be avoided. .

Since the claw 35 is provided at the tip of the arm 29,
When assembling the slide gear 213 to the retainer 25, when inserting the arm 29 into the toothless portion 229 of the slide gear 213, it is necessary to bend the arm 29 largely outward so that the claw 35 does not contact. .

However, the insertion portion 33 has a notch 3
By providing 9, the width is narrower than that of the base 31, and the flexibility is greatly improved.

Therefore, the retainer 25 and the slide gear 21
3, and the workability is improved.

Further, even if the width of the insertion portion 33 is narrowed,
Is not changed, so that the strength of the arm 29 does not decrease.

Next, a third embodiment of the present invention will be described with reference to FIGS. Each of the figures shows a retainer 43 and a slide gear 213 used in the hub clutch of this embodiment, and this embodiment has the features of claims 1 and 4.

As shown in the figures, the retainer 43 is formed by a flange portion 45 and two arms 47 provided at equal intervals from each other. Each arm 47 is connected to the base 4 on the flange 45 side.
9 and an insertion portion 51 on the distal end side of the base 49, and a claw 53 bent inward is provided at the distal end of each insertion portion 51. The insertion portion 51 of each arm 47 is inserted into the toothless portion 229 of the slide gear 213.

As shown in FIG. 7, the insertion portion 51 of the retainer 43 has a notch 57 whose width increases toward the distal end while leaving a contact portion 55 with the toothless portion 229 on the base 49 side.
Are provided at the edges on both sides, so that the contact portion (contact portion 55) between the insertion portion 51 and the toothless portion 229 is provided.
Is moved to the base 49 side.

Thus, the hub clutch according to the third embodiment is configured.

The arrow 59 in FIG. 7 indicates the position of the force applied to the base 49 of the arm 47 during ratcheting until the phase is matched when the slide gear 213 meshes with the drive gear 209.

The moment applied to the base 49 of the retainer 43 during ratcheting is such that the contact point between the arm 47 and the toothless portion 229 is smaller than the conventional example by the distance moved toward the base 49. Therefore, the force applied to the base 49 is reduced accordingly, cracks and deformation are prevented, and the function of the hub clutch can be normally maintained for a long time.

Therefore, it is not necessary to take measures such as making the retainer 43 thick, and it is possible to avoid cost increase and weight increase.

Further, since the notch 57 is provided on the retainer 43 side in order to move the contact portion to the base 49 side, the slide gear 213 does not need to be changed, and the cost increase due to the change can be avoided. .

Also, as in the case of the retainer 25, the insertion portion 51 has a width smaller than that of the base portion 49 due to the provision of the notch 57 at the edge, and the flexibility is greatly improved. There is no risk of deformation even if it is greatly bent.

Therefore, the retainer 43 and the slide gear 21
3 is easy, and workability is improved.

Further, even if the width of the insertion portion 51 is narrowed,
Is not changed, so that the strength of the arm 47 does not decrease.

In the present invention, the operation means of the slide gear is not limited to the cam mechanism shown in FIG. 8, but may be, for example, an actuator using air pressure.

[0085]

According to the first aspect of the present invention, as described above, a gap is formed between the arm (insertion portion) of the retainer and the engagement groove of the slide gear on the distal end side of the insertion portion. By moving the contact point between the insertion portion and the engagement groove toward the base of the arm, the moment applied to the base of the retainer is reduced, so that the arm can be ratcheted between the slide gear and the drive gear. The force on the base of the is reduced accordingly,
Cracks and deformation of the retainer are prevented, and the function of the hub clutch is normally maintained for a long time.

Therefore, it is not necessary to take measures such as increasing the thickness of the retainer, thereby avoiding an increase in cost and weight.

According to the second aspect of the invention, the same effect as that of the first aspect is obtained, and the notch is provided in the engagement groove of the slide gear. Therefore, the retainer does not need to be changed, and the cost associated with the change is not required. Ascent is avoided.

According to the third aspect of the present invention, the same effect as that of the first aspect is obtained, and the notch is provided on the insertion portion side of the retainer. Ascent is avoided.

Further, since the insertion portion has a notch in the edge portion, the width of the insertion portion becomes narrower than that of the base portion, and the flexibility is greatly improved. Even if the insertion part is greatly bent so that the claws do not hit, there is no possibility that the arm will be deformed, and the assembly will be easy,
Workability is improved.

Further, even if the width of the insertion portion is reduced, the width of the base is not changed, so that the strength of the arm does not decrease.

According to the fourth aspect of the present invention, the same effect as that of the first aspect is obtained, and similarly to the third aspect, the retention is achieved.
Since the notch is provided on the insertion part side of the screw, the slide gear does not need to be changed, and the notch provided on the edge greatly improves the flexibility of the insertion part. There is no possibility that the arm will be deformed even if the arm is greatly bent, the assembling is easy, and the workability is improved.

[Brief description of the drawings]

FIG. 1 is a front view showing a state in which a slide gear is attached to a retainer used in a first embodiment of the present invention.

FIG. 2 is a view taken in the direction of arrow A in FIG. 1;

FIG. 3 is a perspective view showing a main part of the first embodiment.

FIG. 4 is a front view showing a state where a slide gear is attached to a retainer used in a second embodiment of the present invention.

FIG. 5 is a view taken in the direction of arrow B in FIG. 4;

FIG. 6 is a front view showing a state where a slide gear is attached to a retainer used in a third embodiment of the present invention.

7 is a view as viewed in the direction of arrow C in FIG. 6;

FIG. 8 is a sectional view of a conventional example.

FIG. 9 is a front view showing a state in which a slide gear is attached to a retainer used in a conventional example.

FIG. 10 is a sectional view taken along line DD of FIG. 9;

FIG. 11 is a view taken in the direction of arrow E in FIG. 9;

[Explanation of symbols]

 1, 25, 43 Retainer 3, 213 Slide gear 5, 27, 45 Retainer flange 7, 29, 47 Retainer arm 9, 31, 49 Base of arm 11, 33, 51 Arm insertion Part 13, 35, 53 Claw of insertion part 15, 215 Spline of slide gear 17, 229 Tooth missing part (engagement groove) of slide gear 19 Thick part of slide gear 21, 37, 55 Contact part 22 Gap 39 Insertion direction Notch 57 Notch increasing in width toward the tip 203 Housing 207 Drive shaft 209 Drive gear 211 Spline 257 of housing Cam mechanism (operating means)

Claims (4)

[Claims] A housing fixed to a wheel hub on a wheel side, a drive gear fixed to a drive shaft, a spline on an outer periphery meshes with a spline on an inner periphery of the housing, and a coupling position meshing with the drive gear and the meshing position. A slide gear that can be moved to a connection release position where the slide gear is released, and a plurality of arms formed in the flange portion through the base portion are inserted through engagement grooves provided on the outer periphery of the slide gear,
A retainer formed at the tip of each arm to lock the slide gear with an inwardly bent claw; and operating means for moving the slide gear to the connection position via the retainer; By forming a gap between the engagement groove and the opposite side of the base while leaving a contact portion on the base side of the arm, the contact point between the insertion portion and the engagement groove is moved to the base side. And a hub clutch. 2. The insertion part according to claim 1, wherein in the engagement groove of the slide gear, the base side of the spline teeth on both sides is made thicker, or a cutout is provided on the opposite side of the base part. A contact portion between the hub clutch and the engagement groove has been moved to a base portion side. 3. The invention according to claim 1, wherein a notch parallel to the insertion direction is provided at both edges of the insertion portion to move a contact portion between the insertion portion and the engagement groove toward the base. A hub clutch, characterized in that: 4. The invention according to claim 1, wherein a notch which becomes wider toward the tip is provided at both edges of the insertion portion so that a contact portion between the insertion portion and the engagement groove is provided on the base side. A hub clutch that has been moved to