JPH07224859A - Conical clutch device for automatic transmission - Google Patents

Abstract

PURPOSE:To perform constant regulation of rotation in a given direction and selective regulation of opposite rotation by providing an annular first member having a conical friction surface, an annular second member engageable with the annular first member, and an actuator reinforcing engagement between the two annular members. CONSTITUTION:When an oil pressure is not fed to a pressure chamber 14, a press force is not exerted on an inner ring 7 from a piston 12 by a return spring 13 and rotation torque of a planetary carrier 1 is transmitted to the inner ring 7 through a second friction surface 7a engaged with the first friction surface 4c of an intermediate member 4 and further to an outer ring 8 through a helical spline 9. During normal rotation of the carrier 1, the intermediate member 4 is nipped between the friction surface 7a and the nip friction surface 8a of an outer ring 8 by means of thrust and the carrier 1 is fixed to a case 3. During reversing of the carrier 1, the inner ring 7 is separated away from an intermediate member 4 by means of thrust and the carrier 1 is rotated. When an oil pressure is fed to the pressure chamber 14 by reversing torque of the carrier 1, the carrier 1 is fixed to a case 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a conical clutch device for fixing and releasing a rotating body of an automatic transmission.

[0002]

2. Description of the Related Art FIG. 4 is a skeleton view of a conventionally known automatic transmission. As a means for fixing a front planetary carrier 01 to a case 02 as a reaction force element, a low one-way clutch 03 and a low gear clutch 03 are used. An AND reverse brake 04 is provided. The low-and-reverse brake 04 drives and engages a piston (actuator) (not shown) when shifting to the reverse speed, and the low-one-way clutch 03 has a predetermined direction (relative to the front planetary carrier 01). The first step forward
It operates only when the rotational torque is input in the rotational torque input direction during high-speed acceleration state, fixes the front planetary carrier 01 to the case 02, and allows the front planetary carrier 01 to rotate in the opposite direction. (For example, see page I-61 of "Maintenance Manual RE4R04 type" issued by Nissan Motor Co., Ltd. in March 1988).

Further, as a friction engagement element used in an automatic transmission, there is known one having a conical clutch device as disclosed in, for example, Japanese Utility Model Laid-Open No. 1-115049. In this conventional conical clutch device, a conical friction surface is provided on each of the annular first member movably supported by the rotating body in the axial direction and the annular second member movably supported by the case in the axial direction. When the actuator is driven to move the annular second member, the friction surfaces strongly abut and engage with each other.At this time, the friction surfaces gradually slide by the conical surface and the friction engagement force gradually increases. It has an excellent engagement characteristic that it is possible to absorb a sudden torque change, and the occurrence of shift shock can be prevented.

[0004]

By the way, as in the former prior art, the rotating body is fixed to a reaction force element such as a case without rotating in a predetermined direction, but is allowed to rotate in the opposite direction. In providing a function and a function of restricting rotation in the opposite direction only when necessary, two means, a clutch (low and reverse brake) operated by an actuator and a one-way clutch, are used as means for fixing the rotating body. Since it is provided, there is a problem that the number of parts is increased, resulting in an increase in cost and weight and an increase in size of the entire device.

Further, the latter prior art also has good engagement characteristics, but does not have the above-mentioned two functions.

The present invention has been made by paying attention to the above-mentioned conventional problems, and one cone clutch device having a good engagement characteristic can constantly regulate the rotation of the rotating body in a predetermined direction. , And its purpose is to allow both selective regulation of rotation in the opposite direction.

[0007]

In order to achieve the above object, a conical clutch device of an automatic transmission according to the present invention is connected to an outer peripheral spline formed on the outer peripheral side of a rotating body and has a conical first friction. An annular first member having a surface, an annular second member having a second friction surface engageable with the first friction surface, and a spline formed on the outer peripheral side of the annular second member are fitted together. A helical spline is formed on the inner diameter side, and a fixing member that is engaged with the housing member on the outer diameter side and whose rotation is restricted, and the annular second member in a direction that strengthens the engagement with the annular first member. A moving actuator is provided.

The rotating body is, for example, a planetary gear device (claim 2).

A friction surface may be formed between the fixing member and the annular first member (claim 3).

Further, the annular elastic member is elastically deformed so as to urge one of the annular first member and the annular second member in a direction in which engagement is strengthened by a restoring force in a direction of reducing the outer diameter. In this state, it may be mounted on the outer circumference of any one of the annular first member, the annular second member, and the rotating body (claim 4).

Further, in the annular elastic member according to a fourth aspect of the present invention, an annular slant surface is formed on a side of the outer peripheral portion of the rotating body on which the outer peripheral spline is formed, facing the actuator, and the annular slant surface and the annular first member. The elastic member may be mounted in the elastic member mounting groove formed by the plane orthogonal to the axial direction (claim 5).

Alternatively, the annular elastic member according to claim 4 is mounted in an elastic member mounting groove formed on the outer periphery of the member arranged on the outer diameter side of the annular first member and the annular second member. May be. (Claim 6).

[0013]

When the rotational torque is input to the rotating body when the actuator is not driven, the rotational torque is input to the annular first member and then engaged with the first friction surface of the annular first member. Is transmitted to the annular second member via the second friction surface,
Further, it is transmitted to the fixed member fitted with the annular second member via the helical spline.

At this time, in the helical spline, a thrust is generated in the axial direction and acts relatively on the fixed member and the annular second member, that is, this thrust corresponds to the direction of the rotational torque. The second member acts to strengthen the engagement with the annular first member, or conversely acts to weaken the engagement. Therefore, according to the direction (forward / reverse) of the rotational torque input to the rotating body, the engagement of the annular members is strengthened in one of the forward and reverse directions to restrict the rotation of the rotating body, and the other of the forward and reverse directions is performed between the annular members. The engagement is weakened and the rotating body rotates.

Next, when the actuator is driven in the state where the rotational torque is transmitted in the direction in which the rotation of the rotating body is permitted, the actuator moves against the thrust generated by the helical spline. The member is moved to engage the annular first member. Therefore, the rotating body is fixed to the reaction force element.

In the apparatus according to the third aspect, the friction surface is formed between the fixing member and the annular first member, and when the thrust in the direction that strengthens the engagement is generated in the helical spline, the fixing member is formed. Since the thrust acts in the direction in which the and the annular second member relatively approach, the annular first member,
It engages with both the annular second member and the fixed member. Therefore, the fixing of the rotating body becomes more reliable.

Next, in the apparatus according to the fourth aspect, when the rotating body is not rotating, the annular first member or the second annular member is urged by the annular elastic member in the direction in which the engagement between the two members is strengthened. ing. Therefore, as described above, when the direction of the rotational torque of the rotating body is the direction in which the annular first and second members are engaged by the thrust generated by the helical spline, this engagement is performed by the urging force. It can be done reliably.

On the other hand, when the rotating body is rotating, the rotating torque is transmitted from the rotating body side to the annular elastic member, and the centrifugal force generated thereby is in the direction opposite to the acting direction of the restoring force on the annular elastic member. The urging force that acts to widen the outer diameter of the ring and that acts to engage both the annular first and second members is eliminated, and dragging caused by friction between the friction surfaces during rotation of the rotating body is prevented. can do.

The action of the centrifugal force of the rotating body on the elastic member will be described more specifically. In the apparatus according to the fifth aspect, the outer diameter of the annular elastic member is reduced when the rotating body is not rotating. The restoring force acting changes the direction in the thrust direction by the ring slope and presses the annular first member to urge the engagement of both the annular first and second members. On the other hand, when the rotating body rotates, the annular elastic member mounted on the outer periphery of the rotating body also rotates, and the centrifugal force acts in such a direction as to widen the inner diameter of the annular elastic member, and the biasing force acts on the annular first member. It will be in a non-use state, and dragging can be prevented.

Further, in the apparatus according to the sixth aspect, when the rotating body is not rotating, the restoring force of the annular elastic member tightens the members arranged on the outer diameter side of the annular first and second members in the inner diameter direction. Acting in a positive direction, which urges engagement with the member on the inner diameter side. On the other hand, when the rotating body rotates, a rotational torque is input from the rotating body side and the centrifugal force acts in a direction to widen the inner diameter of the annular elastic member, and the biasing force does not act in the direction to strengthen the engagement and drag can be prevented. .

[0021]

Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view showing an essential part of an automatic transmission AT to which a conical clutch device A for an automatic transmission according to a first embodiment of the present invention is applied, in which 1 is a planetary carrier as a rotating body. . This planetary carrier 1 is a planetary gear device PG.
This planetary gear device PG is supported by the outer periphery of the output shaft 2 of the automatic transmission AT and receives the rotational torque from another planetary gear device (not shown).
And a plurality of planetary gears P1 meshing with the sun gear S1, a planetary carrier 1 supporting the planetary gears P1, and a ring gear R1 meshing with the planetary gear P1.

The device A of the first embodiment corresponds to the invention of claim 5, and is for fixing the planetary carrier 1 to the case 3 as a housing member, and has an intermediate portion on the outer periphery of the planetary carrier 1. The members 4 are joined. The intermediate member 4 corresponds to the annular first member in the claims, and as shown in the enlarged view of FIG. 2, a substantially annular ring portion 4a having a conical surface and the right end of the ring portion in the drawing. Flange portion 4b protruding in the axial direction from the inner circumference of the portion
And the flange portion 4b is connected to the outer periphery of the planetary carrier 1 by an outer peripheral spline 5 in the axial direction. Further, the ring portion 4a has a first friction surface 4c formed on the inner peripheral conical surface thereof, and a locking projection 4d formed on the right side of the flange portion 4b in the drawing.

Here, the structure of the connecting portion between the intermediate member 4 and the planetary carrier 1 will be described in detail. On the outer periphery of the planetary carrier 1, a ring sloped surface is inclined so that the left side of the drawing is closer to the axial center of the lower side in the drawing. 1a is formed.
A C-shaped spring (annular elastic member) 6 is mounted in a spring mounting groove 30 surrounded by the outer circumference of the ring sloped surface 1a, the flange portion 4b of the intermediate member 4 and the locking projection 4d. That is, the spring 6 is formed in a substantially C shape with a part of the annular shape cut away, and is configured to generate a restoring force when a force is applied in a direction in which the inner diameter is changed,
It is mounted on the outer periphery of the planetary carrier 1 at a position where it comes into contact with the right end surface of the flange portion 4b of the intermediate member 4 in the figure in a state where the inner diameter is widened (a biasing force is generated in the direction of tightening the planetary carrier 1) Has been done.

An inner ring 7 is provided on the inner circumference of the intermediate member 4. The inner ring 7 corresponds to the annular second member in the claims, and is formed in a conical surface shape on the inside and outside, and the second portion engaging with the first friction surface 4c is formed on the right side portion of the outer periphery in the drawing. A friction surface 7a is formed.

The left end of the outer circumference of the inner ring 7 in the figure is connected to the inner ring 7 and the outer ring 8 arranged outside the intermediate member 4. That is, the outer ring 8 corresponds to the fixing member in the claims, and is connected to the inner ring 7 by the helical spline 9, while the outer peripheral portion is connected to the case 10 as a reaction element by the axial spline 10. It is slidably supported on the case 3 in the axial direction (the arrow RL direction in the drawing). On the right side of the inner circumference of the outer ring 8 in the figure, a conical sandwiching friction surface 8a that contacts the outer peripheral surface of the intermediate member 4 is formed. In addition, this outer ring 8
The slide in the right direction in the figure is configured to be restricted at a predetermined position by the thrust ring 11.

On the left side of the inner ring 7 in the figure, a piston 12 which constitutes the actuator of the claims is provided. That is, as shown in FIG. 1, the piston 12 is supported by a cylinder 3a formed in the case 3 so as to be movable in the axial direction (RL direction), and is biased leftward in the drawing by a return spring 13. On the other hand, it is configured to be driven rightward in the figure by the hydraulic pressure introduced into the pressure chamber 14, and is configured to press the inner ring 7 rightward in the figure via the disc spring 15 when driven rightward. There is.

Next, the operation of the first embodiment will be described.

A) When the piston is not driven When the hydraulic pressure is not supplied to the pressure chamber 14, the piston 12 is
Is arranged on the left side in the figure by the urging force of the return spring 13, and no pressing force acts from the piston 12 to the inner ring 7.

In this state, when the rotational torque is input to the planetary carrier 1, the rotational torque is applied to the intermediate member 4
Is transmitted to the inner ring 7 via the second friction surface 7a engaging with the first friction surface 4c of the intermediate member 4, and is further coupled from the inner ring 7 via the helical spline 9. Is transmitted to the outer ring 8.

At this time, thrust is generated in the helical spline 9 in the axial direction (RL direction). That is, in the outer ring 8 and the inner ring 7, when the rotational torque input to the planetary carrier 1 is one of the forward and reverse directions (hereinafter, this direction is referred to as the forward rotation direction), it is indicated by an arrow in FIG. As described above, the thrust F _A is generated so as to bring them closer to each other. On the other hand, when the rotation torque is in the reverse rotation direction, a thrust force F _B in the direction for separating them is generated as shown by the arrow in the figure.

Therefore, when the planetary carrier 1 rotates in the normal direction, the thrust F _A causes the intermediate member 4 to move the second friction surface 7 a of the inner ring 7 and the sandwiching friction surface 8 a of the outer ring 8.
The intermediate carrier 4 and the inner ring 7 are engaged with each other, and the planetary carrier 1 is fixed to the case 3. On the contrary, when the planetary carrier 1 is rotated in the reverse direction, the thrust F _B moves the inner ring 7 away from the intermediate member 4 to release the engagement between the intermediate member 4 and the inner ring 7, and the planetary carrier 1 rotates.

The spring 6 is mounted on the ring sloped surface 1a of the planetary carrier 1 with its inner diameter widened. Therefore, in the state where the planetary carrier 1 is fixed by the engagement of the intermediate member 4 and the inner ring 7 described above, the spring 6 tries to slide in the lower left direction in the figure along the ring slope 1a by the urging force. As a result, the intermediate member 4 is pushed, the engagement with the inner ring 7 is strengthened, and the reliability of the engagement is enhanced.

On the other hand, the intermediate member 4 and the inner ring 7
When the planetary carrier 1 rotates due to the disengagement with the planetary carrier 1, the spring 6 mounted on the planetary carrier 1 also rotates, and the centrifugal force generated by the rotation acts in such a direction as to widen the inner diameter of the spring 6. Therefore, the urging force of the spring 6 is weakened and does not act on the intermediate member 4, and it is possible to prevent the intermediate member 4 and the inner ring 7 from being engaged with each other, that is, "drag" due to the urging force of the spring 6. When the centrifugal force increases, the spring 6
The intermediate member 4 may be displaced from the planetary carrier 1 by shifting the position to the right in the figure along the ring slope 1a.
This can be prevented by the locking projection 4a.

B) When the piston is driven When rotational torque is input to the planetary carrier 1 in the reverse direction and hydraulic pressure is supplied to the pressure chamber 14 while the planetary carrier 1 is rotating, the piston 12 causes the inner ring 7 to move, Press to the right, the inner ring 7 is the intermediate member 4
Engage with. Therefore, the planetary carrier 1 is fixed to the case 3.

As described above, the device A of the first embodiment drives the piston 12 and the conventional one-way clutch function of permitting the reverse rotation of the planetary carrier 1 and restricting the reverse rotation of the planetary carrier 1 to fix it to the case 3. It also has the function of a conventional clutch (brake) for stopping the reverse rotation of the planetary carrier 1 by combining the two conventional functions into one, and it is possible to reduce the number of parts and the weight, and it is compact. The effect that it can be achieved is obtained.

In addition, in the device A of the first embodiment, the inner ring 7 and the outer ring 8 are arranged inside and outside the intermediate member 4 having the first friction surface 4c for engagement, and both rings 7, 8 are arranged. A helical spline 9 is provided between the
Since the intermediate member 4 is sandwiched between the rings 7 and 8, not only the intermediate member 4 and the inner ring 7 contact with each other with the thrust F _A , but also the intermediate member 4 is moved from the back surface to the engagement side by the outer ring 8. The effect of being pressed and high engagement performance is obtained.

Further, in the first embodiment, when the planetary carrier 1 is fixed, the spring 6 for urging the intermediate member 4 in the engaging direction is provided to improve the engaging performance. Moreover, when the planetary carrier 1 is rotated, the urging force of the spring 6 does not act on the intermediate member 4 due to the centrifugal force, and the effect of preventing "drag" can be obtained.

Next, a second embodiment of the present invention will be described. In describing the second embodiment, the same components as those in the first embodiment are designated by the same reference numerals and the description thereof will be omitted.
Regarding the operation, only the differences will be described.

FIG. 3 shows a second embodiment of the invention according to claim 6.
It is a schematic diagram which shows the conical clutch apparatus B of the automatic transmission of an Example.

An inner ring 21 corresponding to the annular first member in the claims is joined to the outer peripheral portion of the planetary carrier 1. A conical first friction surface 21 a is formed on the outer peripheral surface of the inner ring 21. Further, the inner ring 21 is movable in the axial direction with respect to the planetary carrier 1, but the movement in the left direction in the drawing is limited to the case 3
It is configured to be restricted at a predetermined position by a stopper 3c (not shown) formed on the.

An outer ring 22 is provided on the outer circumference of the inner ring 21. This outer ring 22
It corresponds to the annular second member in the claims and has a second friction surface 22a formed on the inner periphery thereof to engage with the first friction surface 21a. The outer ring 22 is configured such that a pressing force F is input when a piston (not shown) similar to that of the first embodiment is driven.

A fixing member 23 is joined to the outer circumference of the outer ring 22. The inner peripheral side of this fixing member 23 is connected to the outer ring 22 by a helical spline 24, while the outer peripheral side thereof is connected to the case 3 by an axial spline 10. Further, the case 3 is provided with a thrust ring (stopper) 11 that restricts the fixing member 23 from sliding rightward in the drawing.

A spring mounting groove 22b is formed on the outer circumference of the outer ring 22, and a C-shaped spring 6 is mounted in the spring mounting groove 22b with its inner diameter widened. And the end of this spring 6 is
Protruding portion 21 of inner ring 21 capable of transmitting rotational torque
engaged with b.

Next, the operation of the second embodiment will be described. a) When the piston is not driven When the planetary carrier 1 is normally rotated, the rotational torque is transmitted from the inner ring 21 to the outer ring 22 via both friction surfaces 21a and 22a, and further, the fixing member 23.
Is transmitted to the helical spline 24 at this time, a thrust F _A indicated by an arrow in the drawing is generated. Then, the fixing member 23
The outer ring 22 is thrust by the inner ring 2 by the thrust F _{A as} the slide of the outer ring 22 is restricted by the thrust ring 11.
It is pressed against 1, and both 21 and 22 are engaged. Therefore, the planetary carrier 1 is fixed to the case 3.
At this time, the movement of the inner ring 21 to the left in the drawing is restricted by the stopper 3c.

On the contrary, when the planetary carrier 1 is rotated in the reverse direction, the thrust F _B is generated in the helical spline 24 and the outer ring 22 separates from the inner ring 21.
Therefore, the planetary carrier 1 rotates.

When the planetary carrier 1 is fixed by engaging both the rings 21 and 22, the urging force of the spring 6 is applied to the outer ring 22 by the friction surface 21.
It is inputted in the direction in which the engagement of a and 22a is strengthened, and this engagement can be further ensured. On the other hand, when the planetary carrier 1 is rotated in the reverse direction, a rotational torque is input from the inner ring 21 to the spring 6, a centrifugal force is generated in the spring 6, and the urging force does not act on the outer ring 22. Therefore, "drag" can be prevented.

Although the embodiment has been described above, the specific structure is not limited to this embodiment, and the present invention includes a design change and the like within a range not departing from the gist of the invention. For example, if the annular first member and the annular second member have conical friction surfaces, the overall shape is not limited to the shape of the embodiment.

[0048]

As described above, in the conical clutch device for an automatic transmission according to the present invention, one device always controls the rotation of the rotating body in a predetermined direction and the other direction. Since it is possible to both selectively control rotation, the structure can be simplified, the number of parts and weight can be reduced, and the size can be reduced. Even in this case, it is possible to obtain the effect that good characteristics with less shock can be obtained.

Further, in the apparatus according to claims 4, 5, and 6, an annular elastic member for urging the engagement between the annular first member and the annular second member is provided, and the annular elastic member is further provided with the annular elastic member. Because the centrifugal force acts against the biasing force,
First and second when the operation to fix the rotating body is being performed
It is possible to prevent the occurrence of "drag" by preventing the biasing force from acting when the rotating body is rotated, while making it possible to more reliably engage the two members.

Further, in the apparatus according to the third aspect, a friction surface is formed between the fixed member and the annular first member to generate thrust in the direction of engaging the annular splines with the helical first and second members. At this time, since the annular first member is also engaged by the fixing member, high engagement performance can be obtained.

[Brief description of drawings]

FIG. 1 is a sectional view showing a main part of an automatic transmission to which a conical clutch device for an automatic transmission according to a first embodiment of the present invention is applied.

FIG. 2 is an enlarged view of a main part of FIG.

FIG. 3 is a schematic diagram showing a conical clutch device of an automatic transmission according to a second embodiment of the present invention.

FIG. 4 is a skeleton diagram showing a configuration of a conventional automatic transmission.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Planetary carrier (rotating body) 1a Ring slope 3 Case (housing member) 4 Intermediate member (annular first member) 4c First friction surface 5 Outer peripheral spline 6 Spring (annular elastic member) 7 Inner ring (annular second member) 7a Second friction surface 8 Outer ring (fixing member) 8a Nip friction surface 9 Helical spline 10 Axial spline 12 Piston (actuator) 21 Inner ring (first annular member) 21a First friction surface 22 Outer ring (second annular member) 22a Second friction surface 22b Spring mounting groove 23 Fixing member 24 Helical spline 30 Spring mounting groove

Claims (6)

[Claims] 1. An annular first member coupled to an outer peripheral spline formed on the outer peripheral side of a rotating body and having a conical first friction surface, and a second friction surface engageable with the first friction surface. And a helical spline that fits with a spline formed on the outer peripheral side of the annular second member is formed on the inner diameter side and engages with the housing member on the outer diameter side to rotate. A conical clutch device, comprising: a fixed member that is restricted by the actuator; and an actuator that moves the annular second member in a direction that strengthens the engagement with the annular first member. 2. The conical clutch device for an automatic transmission according to claim 1, wherein the rotating body is a planetary gear device. 3. A friction surface is formed between the fixing member and the annular first member.
Alternatively, the conical clutch device of the automatic transmission according to the item 2. 4. The annular elastic member is elastically deformed so as to urge one of the annular first member and the annular second member in a direction in which engagement is strengthened by a restoring force in a direction of reducing the outer diameter. 4. The automatic transmission according to claim 1, wherein in the state, one of the annular first member, the annular second member, and the rotating body is attached to the outer periphery of the rotating body so that rotational torque can be input from the rotating body side. Conical clutch device. 5. A ring slant surface is formed on a side of the outer peripheral portion of the rotating body on which the outer peripheral spline is formed, the side facing the actuator, and the elastic member mounting member is formed by the ring slant surface and a plane orthogonal to the axial direction of the ring-shaped first member. 5. A cone of an automatic transmission according to claim 4, wherein a groove is formed, and the annular elastic member is mounted in the elastic body mounting groove in a state where one end of the annular elastic member is engaged with a rotating body in a rotational direction. Clutch device. 6. An elastic member mounting groove is formed in a member of the annular first member and the annular second member that is disposed on the outer diameter side, and the annular elastic member is mounted in the elastic member mounting groove. The conical clutch device for an automatic transmission according to claim 4, wherein: