JP3168906B2 - Clutch device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a clutch device, and more particularly to a clutch device used in an automatic transmission.

[0002]

2. Description of the Related Art The present applicant has previously filed Japanese Patent Application No. 7-66252.
, A cam mechanism is provided between members that rotate relative to each other in the circumferential direction, and the cam mechanism converts a circumferential force generated by the relative rotation between the members into an axial thrust, which is used as a clutch engagement force. We have applied for a clutch device. The above-mentioned device makes it possible to reduce the number of clutch disks by utilizing the boosting function and the unidirectionality of the cam mechanism, and to reduce the size of the entire clutch device by eliminating the one-way clutch.

[0003]

In the clutch device described above, the cam force is generated by a piston operated by hydraulic pressure, the cam mechanism is pressed integrally to a rotating member, and the cam farther from the piston is dragged by the rotating member. This is accomplished by inducing relative rotation between the cam members. However, there is a problem that it takes a long time from the actuation of the piston to the occurrence of the above-mentioned drag due to the play between the components, resulting in poor response. To solve this problem,
It is conceivable to apply a weak oil pressure to the piston so that the above-mentioned cam action does not occur.
It is necessary to attach pressure regulating devices such as relief valves, regulator valves, accumulators, etc. to the hydraulic circuit,
There is a problem that cost increase due to the complexity of the hydraulic circuit and increase in the number of parts cannot be avoided.

SUMMARY OF THE INVENTION In view of the above problems, an object of the present invention is to improve the response of a clutch device using a cam mechanism with a simple configuration and without cost.

[0005]

According to the first aspect of the present invention, a pair of cam members are disposed between a pair of members which are spaced apart from each other on a common axis and rotate relatively to each other. In a clutch device in which one of a pair of cam members is pressed against one of the pair of relatively rotating members to rotate relatively in a predetermined direction to generate a cam force, and the relatively rotating member is engaged by the cam force. In addition, there is provided a clutch device in which the initial movement means presses one of the pair of cam members with a mechanical force not using a fluid force.

In the clutch device configured as described above, one of a pair of cam members disposed between a pair of members that are spaced apart from each other on a common axis and relatively rotated by one another is relatively rotated by mechanical force. The pair of members which are relatively rotated by the cam force generated by being pressed by one of the pair of members and relatively rotating in the predetermined direction are engaged.

According to a second aspect of the present invention, there is provided the clutch device according to the first aspect of the present invention, wherein the mechanical force generated by the initial movement means is used as the urging force of the spring member.

In the clutch device constructed as described above, one of the pair of cam members is pressed against one of the pair of relatively rotating members by the urging force of the spring member, and as a result, the pair of cam members are moved in the predetermined direction. A cam force is generated by relatively rotating the pair of members, and the pair of members relatively rotated by this cam force are engaged.

According to a third aspect of the present invention, in the first aspect of the present invention, the mechanical force generated by the initial movement means is obtained by moving one of the pair of cam members in the same state with respect to the other. Is provided.

In the clutch device configured as described above, one of the pair of cam members is relatively rotated by the inertial force obtained by moving one of the pair of cam members in the same state with respect to the other. The pair of members are pressed against one of the members, and as a result, the pair of cam members are relatively rotated in a predetermined direction to generate a cam force, and the pair of members relatively rotated by the cam force are engaged.

[0011]

Embodiments of the present invention will be described below with reference to the accompanying drawings. First, FIG. 1 schematically shows an entire conventional automatic transmission in order to explain to which part of the entire conventional automatic transmission the embodiment of the present invention is applied. . In FIG. 1, AT indicates the entire transmission mechanism of the conventional automatic transmission.
Basically, it is composed of three planetary gear units and friction engagement elements for connecting and disconnecting respective elements such as a ring gear, a sun gear and a carrier. The details are as follows.

[0012] Incidentally, in the description, the direction of rotation be those viewed from the side of the input shaft X _i, right rotation means clockwise rotation, left rotation indicates counterclockwise rotation. X _i is an input shaft, which is connected to an output shaft (not shown) of a torque converter (not shown). PG ₁ , PG ₂ and PG ₃ are a front planetary gear unit, a rear planetary gear unit, and an OD (OD is an overdrive) planetary gear unit, respectively.

R ₁ , R ₂ and R ₃ are a front planetary ring gear, a rear planetary ring gear and an OD planetary ring gear, respectively. K ₁ , K ₂ and K ₃ are a front planetary carrier, a rear planetary carrier and an OD planetary carrier, respectively. S ₁₂ is the front planetary gear unit, is a common front & rear planetary sun gear to the rear planetary gear unit,
S ₃ is a OD planetary sun gear.

[0014] C ₁ is a first clutch and disengaging the input shaft X _i and the front planetary ring gear R _1. C ₂ is a second clutch and disengaging the input shaft X _i and the front and rear planetary sun gear S _12. C ₃ is a third clutch for connecting and disconnecting the OD planetary carrier K ₃ and the OD planetary sun gear S ₃ .

B ₁ is the first brake, which is
To lock the rear planetary sun gear S _12. B ₂ is second
A first one-way clutch F
To lock the left rotation of the front and rear planetary sun gear S ₁₂ through the _1. B ₃ is a third brake to lock the rotation of the rear planetary carrier K ₂ (there is a right rotation and left rotation by operating conditions). B ₄ is a fourth brake, which locks the rotation of the OD planetary sun gear S ₃ (there are right rotation and left rotation by operating conditions).

F ₁ is a first one-way clutch,
The second brake B ₂ is to lock the left rotation of the front and rear planetary sun gear S ₁₂ when you are working. F ₂ is the second
A one-way clutch, to lock the left rotation of the rear planetary carrier K _2. F ₃ is a third one-way clutch, which is an O with respect to the OD planetary sun gear S ₃ .
To lock the left rotation of D planetary carrier K _3. Note that CG ₁ is a counter drive gear, and CG ₂ is a counter driven gear for guiding engine output to a subsequent mechanism, and is not related to the shift itself.

The devices of the first to fourth embodiments which will be described below serve the role of the third brake B ₃ and the second one-way clutch F ₂ among the above, and include the D range,
Range, to lock the counterclockwise rotation of the rear planetary carrier K ₂ in the drive traveling first speed stage of the L range, the first L range
Fast locks the clockwise rotation of the rear planetary carrier K ₂ in the driven running (engine brake state) stage, also locks the clockwise rotation of the rear planetary carrier K ₂ in driving the travel of R-range, the driven vehicle is traveling it is necessary to lock the counterclockwise rotation of, also, D-range, 2-range, at the time of shifting from the first speed stage of the L range to the second speed stage, when the direction of the allotted torque of the rear planetary carrier K ₂ is inverted simultaneously the rear planetary carrier K ₂ is transferred immediately from the left rotation lock state in the right rotation idle state, and at the time of shifting from the second speed stage to the first speed stage, the rear planetary carrier K ₂ is inverted from clockwise to counterclockwise rotation At the same time, rear planetary carrier K
It is required to lock ₂ .

FIG. 3 shows a first embodiment of the clutch device according to the present invention.
Third brake B incorporating the form of _ThreePart automatic transmission
FIG. In FIG. 3, B_ThreeHousing 101
Are formed integrally with the transmission case 500.
And B_ThreeB in the annular concave portion of the housing 101_ThreeFixie
102 is slidably disposed in the axial direction._ThreePiston 1
B to face 02 in the axial direction_ThreePressure plate
103 is provided. B_ThreePiston 102 and B_ThreeStep
On the opposite side of the lesser plate 103,
The cam surface 152 and the cam surface 153 are formed at a plurality of locations in the circumferential direction.
And a cam roller 104 is interposed between them.
You.

[0019] Between the B ₃ piston 102 and B ₃ the pressure plate 103, the initial motion spring 105 to expand and contract in the direction of rotation have been arranged, as described later, by the initial spring 105, use hydraulic force You can create a chance to gain cam power without using it. Also, B
_{The three} pistons 102 are constantly urged leftward in the figure by a return spring 106 that expands and contracts in the axial direction.
The movement in the rotation direction is restricted by the stopper 107.

Meanwhile, B ₃ clutch disc 108 is mounted axially slidably in the coupling member 109 rotates integrally with the rear planetary carrier K ₂ of the rear planetary gear PG _2, also, B ₃ a separator plate 110 is the transmission casing 500 It is mounted so that it can slide in the axial direction and cannot rotate. However, the rightmost one in the figure is restricted from moving to the right. Therefore, B ₃
Clutch disc 108 and B ₃ separator plate 11
0 clutch device 1 is engaged with each other when they are brought axially extending, B ₃ clutch disc 108 locks the rotation of the rear planetary carrier K ₂ is stopped.

As will be described later, no cam force is generated.
B_ThreeClutch disk 108 and B_ThreeSeparee
Plate 110 must be engaged,
B_ThreePiston 102 and B_ThreeOf the pressure plate 103
Oil for supplying hydraulic oil to oil chamber 111 formed therebetween
The path 101a is formed inside the clutch housing 101.
Have been. In addition, the engagement force by hydraulic pressure of hydraulic oil was increased.
In order, B_ThreeHousing 101 and B _ThreeBetween pistons 102
May be provided with a booster cam.

[0022] Figure 4 is a view of the B ₃ pressure plate 103 from the input shaft X _i side, are the partial cross-sectional view as it can be seen the actual arrangement of the initial spring 105. That is, the initial movement spring 105 is B
₍₃₎ a wall surface 103b in the rotation direction of the concave portion 103a formed inside the pressure plate 103 along the rotation direction;
It is disposed between the protrusions 102a formed integrally with the B ₃ piston 102.

Next, the first embodiment configured as described above
Movement of the cam part for the operation of the clutch device
This will be mainly described. First, FIG. 5 shows the P range or N range.
Rear planetary carrier K like a range _TwoDoes not rotate
Or B_ThreeClutch disc 108 stops
Indicates the state of the cam part.
And viewed along the line V-V in FIG.
Fig. 2 schematically shows a cross section viewed outward in the radial direction. In addition,
This clutch device is a so-called wet clutch,
_ThreeClutch disk 108 and B_ThreeSeparator plate 1
10 is arranged in a space filled with oil, and B_Three
Pressure plate 103 and B_ThreeClutch disk 10
There is an oil film between the contact surfaces 8.

In the case of the P range or the N range, no hydraulic oil is supplied to the oil chamber 111. Therefore,
B ₃ The piston 102 is pressed against the B ₃ clutch casing 101 by the biasing force of the return spring 106. On the other hand, B ₃ pressure plate 103 is pushed in the drawing the left by initial spring 105, the cam surface 153 of the B ₃ pressure plate 103 is cam roller 10
4 through up the cam surface 152 of the B ₃ piston 102,
As a result, the back of the B ₃ pressure plate 103 103
c is pressed against the B ₃ clutch disc 108 is,
Since the force of the initial movement spring 105 is set to be weak,
The pressing force is small.

Next, consider a case where the vehicle is shifted from the P range or the N range to any of the D range, the 2 range, and the L range and starts at the first speed. When shifted to the rear planetary carrier K ₂ is a force to be left rotation. This is because, in FIG. 5, B ₃ clutch disc 108 means that attempts to move to the left in FIG.

Then, the B ₃ pressure plate 10
3 moves to the left by being dragged by the B ₃ clutch disc 108 through the oil film, and the B ₃ pressure plate 103
Of the B ₃ piston 10 via the cam roller 104
Up the second cam surfaces, the B ₃ piston 102 and B ₃ pressure plate 103 cams force which tends spaced in the axial direction is generated. As a result, B ₃ pressure plate 103
It is strongly pressed against the B ₃ clutch disc 108.
As a result, the plurality of B ₃ clutch disks 108 come into close contact engagement with the non-rotating B ₃ separator plate 110 and stop. Therefore, is performed locks left rotation of the rear planetary carrier K ₂ is one of the functions required above. In the first embodiment of the present invention, since the starting spring 105 is P range or N range state from B ₃ pressure plate 103 is pressed against the B ₃ clutch disc 108, operation is reliable response Is also fast.

[0027] The above engagement, the force to be Mawaso the B ₃ clutch disc 108 increases as increases, a self-locking manner such engagement. Assuming that the pressing force due to the cam action is F, F = T / (r × tan θ).
However, T is an input torque of the B ₃ pressure plate 103, r is the action of the cam radius, theta is the angle between a plane perpendicular to the cam surface 153 rotation axis.

Next, the above-mentioned rear planetary carrier K ₂
From the 1st gear where the left rotation is locked
Consider a case where gears are shifted to a higher gear. Here, in the second speed,
Rear planetary carrier K ₂ is right rotation. Therefore, when shifting, it is required that a smooth transition can be made from the state in which the left rotation of the first speed stage is stopped to the state of right rotation.

[0029] Here, the clockwise rotation of the rear planetary carrier K ₂ is, B ₃ clutch disc 108 in FIG. 5 means that move right. Rear planetary carrier K ₂ is rotated clockwise, the B ₃ clutch disk 108 moves in the right direction in FIG. 5, B ₃ pressure plate 103 B ₃
The cam surface 153 of the B ₃ pressure plate 103 is moved to the right by being dragged by the clutch disk 108 so that the B ₃ piston 102
The cam surface 152, and as a result, the cam force disappears.

[0030] In this case, acts biasing force of the initial spring 105 to B ₃ pressure plate 103, although B ₃ pressure plate 103 is pressed against the B ₃ clutch disc 108, the force is weak, rear planetary carrier K
₂ can continue spinning clockwise. Between because it is wet clutch B ₃ pressure plate 103 and B ₃ clutch disk 108 is present an oil film, also B ₃ sometimes rotation of the clutch disk 108 is fast, B ₃ pressure plate 103 and the B Judder does not occur between the _three clutch discs 108. Thus, from the state of the first gear, the B ₃ clutch disc 1
The gear can be shifted to the second speed only by reversing 08 to the right, and that state can be maintained.

Conversely, shifting from the second speed to the first speed is as follows:
It can be obtained by simply reversing the left rotation of the rear planetary carrier K ₂ from the right rotation. In this case, the B ₃ clutch disc 108 moving rightward in FIG. 5 is reversed to move leftward, and as a result, the initial movement spring 10
By 5, B ₃ clutch disc 108 B ₃ pressure plate 103 which has sliding contact as described above to instantly engage and B ₃ clutch disc 108, by the force cam force is generated, B ₃ clutch disc 108 is locked to obtain the first speed. Also in this case, the operation of supplying and discharging the hydraulic oil is not required due to the presence of the initial movement spring 105.

On the other hand, when it is driven traveling (engine brake state) in the L range first speed stage, the rear planetary carrier K ₂ is must be locked from attempting to right rotation. A force is applied to the right rotating the rear planetary carrier K _2, B ₃ clutch disc 10 in FIG. 5
Even if 8 moves to the right, the cam force cannot be obtained because it is the same as during the travel of the second speed. Therefore, in this case, by a hydraulic force by supplying hydraulic oil to the oil chamber 111, it is necessary to stop the rotation of the B ₃ clutch disc 108. As described above, B ₃ housing 1
By providing a force multiplying cam between 01 and B ₃ piston 102,
A large force can be obtained with a small hydraulic pressure, and the load on the oil pump can be reduced.

FIG. 6 is a view showing a state of a case of supplying the hydraulic oil to the oil chamber 111 as described above, B ₃ cam surface 152 of the piston 102 via the cam roller 104 B ₃
Cage B ₃ piston 102 and B ₃ pressure plate 103 sliding over the cam surface of the pressure plate 103 is brought into such a state that is closest, B ₃ piston 102 and B ₃ the pressure plate 103 by the hydraulic force together, B ₃ clutch disc 108 pressing the, B ₃ clutch disc 108, and the rear planetary carrier K ₂ connected thereto is locked.

As described above, the first embodiment has the required function, that is, the rear planetary carrier K _2.
Can lock left rotation, rotate right rotation, shift from left rotation lock to right rotation idling, shift from right rotation idling to left rotation lock, lock right rotation and operate when shifting No oil supply / drain operation is required.

FIG. 7 is a diagram schematically showing the structure of the second embodiment. The second embodiment is similar to the first embodiment except that the initial movement spring 105 is replaced by a tension type spring. The operation is also the same as in the first embodiment, and will not be described. In the second embodiment, the recess 10 of the B ₃ pressure plate 103 is used.
Because 3a spring between the wall 103b and the B ₃ piston 102 is not provided, a stopper 113 for preventing the return too far when returning the cam torque in the non-operating direction is applied
Can be easily arranged, for example, as shown by a broken line.

FIG. 8 is a diagram schematically showing the structure of the third embodiment. In the third embodiment, a roller cage 114 for loosely holding the cam roller 104 is provided, and a spring seat 1 formed integrally with the roller cage 114 is provided.
14a and is obtained by arranging the initial spring 105 during the rotation direction of the wall surface 103b of the B ₃ pressure inside the rotational direction recess 103a formed along the plate 103. Other structures are the same as those of the first embodiment.
The operation is also the same as in the first embodiment, and will not be described. In the third embodiment, the amount of expansion and contraction of the initial movement spring 105 is halved compared to the first and second embodiments. This is because, in the first and second embodiments, the initial movement spring 1
In the third embodiment, the roller cage 1 moves in the direction in which both end surfaces of the roller cage 05 move away from each other.
This is because 14 does not move.

FIG. 9 is a diagram schematically showing the structure of the fourth embodiment. The fourth embodiment is a modification of the third embodiment, a recess 102a along the interior in the direction of rotation of the B ₃ piston 102, the roller cage 1
A spring seat 114b formed integrally with the projection 14 protrudes toward the recess 102a, and an initial movement spring 105 is disposed between the wall 102b in the rotation direction of the recess 102a and the spring seat 114b. Other structures are the same as those of the first embodiment. The operation is also the same as in the first embodiment, and will not be described.

Next, a fifth embodiment will be described. In the fifth embodiment, the functions of the third clutch C ₃ and the third one-way clutch F ₃ shown in FIG. 1 are performed. Further, when the state is shifted from the state of the P and N ranges to the D, 2 and L ranges, the O rotates right.
D planetary to re-carrier K ₃ OD planetary sun gear S
₃ is connected immediately, and in the forward speed except the fourth speed in the D range, the connected state is maintained as described above. When shifting from the third speed to the fourth speed, the OD planetary carrier K is used. ₃ and OD planetary sun gear clockwise tighten possibly slipping of S ₃ of the connection immediately released OD planetary carrier K _3, whereas, OD of counterclockwise rotation when shifted P, from the state of the N range to the R range a planetary carrier K ₃ allowed connecting OD planetary sun gear S ₃ in real is required to keep the connection state in the R-range running. Note that the direction of the rotation is the same as the input shaft X _i defined in the description of the first embodiment.
When viewed from the right, if you turn clockwise (clockwise),
The case of turning left (counterclockwise rotation) is the case of turning left.

[0039] FIG. 10 is a cross-sectional view of a third clutch C ₃ moiety incorporating this fifth embodiment. In FIG. 10, C ₃ housing 201 is engaged rotatably with respect to the transmission case 500, OD sun gear S
Combined with ₃ . 202 C ₃ piston 203 C ₃ pressure plate, 204 is a cam roller.
C ₃ piston 202, C ₃ have been splined to the housing 201, to move the cylinder of the annular formed inside the right and left in figure C ₃ housing 201. Further, the inner surface of the C ₃ piston 202 cam surface 252, the inner surface of the pressure plate 203 have been formed in several places cam surface 253 is circumferentially cam roller 204
Facing each other.

The right end position of the return spring 205 is C
During all times view the C ₃ piston 202 is fixed to the _third housing 201 is biased to the left. However,
In the fifth embodiment, the trigger for engagement is obtained by the inertial force, so that the fifth embodiment does not have the initial movement spring as in the first to fourth embodiments. Hydraulic pressure is supplied from the oil passage 201a in the oil chamber 206 between the C ₃ piston 202 and the C ₃ housing 201.

Further, 207 C ₃ clutch disc which is spline-coupled to the OD carrier K _3, 20
8 is a C ₃ separator plates are splined to C ₃ housing 201. The third clutch C ₃ is also a so-called wet clutch, in which the C ₃ clutch disk 207 and the C ₃ separator plate 208 are arranged in a space filled with oil, and the C ₃ pressure plate 203 and the C ₃ clutch disk There is also an oil film between the contact surfaces of 207.

On the other hand, on the outer peripheral side of the C ₃ housing 201, the B ₄ piston 301, B ₄ clutch disc 302 is engaged selectively frictionally engaged with the B ₄ separator plate 303 which is splined to the transmission case 500 Splines are joined.

Next, the operation of the clutch device of the fifth embodiment configured as described above will be described focusing on the movement of the cam portion. First, FIG. 11 but is not spinning is OD planetary carrier K ₃ as P-range or N range, ie viewed C ₃ when the clutch disk 207 is stopped, the states of portions of the cam from the shaft center side FIG.

The operation of the cam portion in each operation state will be described below.
Will be described. In P range and N range, oil passage 201a
Then, hydraulic oil is supplied to the oil chamber 206, and the cam portion is
It is in the state as shown in. From this state, D
OD planet when shifted to 2 range, L range
Tari carrier K_ThreeStarts turning right, but at this time, the OD
Planetary ring gear R_ThreeIs connected to the axle,
In a defined state. This is the planetary gear mechanism,
Carrier input with the ring gear fixed and the sun gear
It is a case where it rotates faster than the carrier. Therefore, O
D planetary sun gear S_ThreeIs OD planetary carrier K
_ThreeIt rotates in the same direction at a faster speed. Therefore, the figure
OD planetary sun gear S at 11_ThreeJoined to
C _ThreePiston 202 is OD planetary carrier K_Three
C connected to_ThreeBefore the clutch disk 207
Line and start moving to the right.

[0045] Then, the cam surface 25 of the C ₃ piston 202
2 up the cam surface 253 of the C ₃ pressure plate 203 via the cam roller 204, the cam force is generated, C ₃ and the pressure plate 203 and the C ₃ piston 202 is spread is that distance C ₃ housing 201 and C ₃ clutch Stretching between the disks 207 results in a state as shown in FIG. Thus, C ₃ housing 201, C ₃
The piston 202 and the C ₃ pressure plate 203 are C ₃
It moves rightward together with the clutch disk 207. Thus, the OD planetary sun gear S ₃ connected to the C ₃ piston 202 rotates clockwise similarly to the OD planetary carrier K ₃ .

The above state is maintained until the third speed in the D range. Then, the shift from the third speed stage to the fourth speed stage is obtained by locking the OD planetary sun gear S ₃ by operating the fourth brake B ₄ from the above state. OD
When the planetary sun gear S ₃ is braked, the OD planetary ring gear R ₃ connected to the axle tries to rotate at the previous speed, so that the OD planetary carrier K ₃ is also reduced. smaller than that of the sun gear S _3, therefore, OD planetary carrier K ₃ is rotated at a faster speed than the OD planetary sun gear S _3. Therefore, in FIG.
C ₃ clutch disc 207 coupled to the planetary carrier K ₃ moves to the right ahead of the C ₃ piston 202 coupled to OD planetary sun gear S _3.

[0047] Thus, in FIG. 12, with respect to C ₃ pressure plate 203 which rotates together with the C ₃ clutch disc 207, C ₃ piston 202 is moved ahead to the right, as a result, the C ₃ piston 202 Cam surface 2
52 down the cam surfaces 253 of the C ₃ pressure plate 203 via the cam roller 204, is engaged in a state as shown in FIG. 13 is released. Then C ₃ piston 2
02 stops. Thus, C ₃ clutch disc 2
Only 07 moves leftward. Therefore, right rotate only OD planetary carrier K _3, the fourth speed stage to stop the OD planetary sun gear S ₃ is obtained. In this manner, in the fourth speed, the OD planetary sun gear S ₃ is in the fourth position.
Locked by the brake B _4, the OD planetary carrier K ₃ are rotated clockwise.

Next, the shift from the fourth speed to the third speed
think of. This is the opposite of the fourth brake B_FourSolve
Obtained by releasing. From the above state,
Rake B_FourRelease OD planetary sun gear S
_ThreeIs connected to the OD planetary pinion gear
Tally ring gear R_ThreeAt the same time as release
Then, turn right. Therefore, in FIG._ThreeC
Using 201 and C_ThreeThe piston 202 moves to the right,
Then C_ThreeThe pressure plate 203 is
And try to stay in the original position, so C_ThreePressure
The cam surface 253 of the plate 203 is
Then C_ThreeAfter going up the cam surface 252 of the piston 202,
And C _ThreePressure plate 203 is C_ThreeClutchday
It contacts the disc 207. Then C_ThreePressure play
203 is C_ThreeDragged by clutch disc 207
It moves to the left in the figure and engages itself with the cam force. The result
Fruit, C_ThreeClutch disk 207 and C_ThreePressure pre
The port 203 comes to rotate as one, and the OD planetary
Sun gear S_ThreeAnd OD planetary carrier K_ThreeIs engaged
And the third speed is obtained.

When shifting from the P range and the N range to the reverse gear, the OD planetary sun gear S ₃ must be meshed with the OD planetary carrier K ₃ rotating left. OD planetary carrier K ₃ is rotated counterclockwise at a speed higher than the OD planetary sun gear S ₃ in the same manner as the case of the right rotation OD planetary carrier K ₃ Left rotation. Thus, C ₃ piston 202 is moved ahead to the left in FIG. 13, the cam force is not generated, the oil chamber 20
And supply hydraulic fluid to the C ₃ piston 20.
2 needs to be engaged with the C ₃ clutch disk 207 via the C ₃ pressure plate 203.

As described above, in the fifth embodiment, the third
At the time of shifting between the first speed and the fourth speed, the moment of engagement can be obtained by the inertial force.

[0051]

According to each of the claims of the present invention, engagement and disengagement can be performed with good response since no hydraulic pressure is used in a clutch device for engaging a relatively rotating member using a cam mechanism. It does not require a complicated hydraulic circuit including an accumulator and the like, and has low cost and high reliability. In particular, according to the third aspect, no additional material is required.

[Brief description of the drawings]

FIG. 1 is a view schematically showing the structure of an automatic transmission according to the related art.

FIG. 2 is a diagram showing a combination of operations of each friction engagement element for obtaining each speed stage in the automatic transmission of FIG.

FIG. 3 is a diagram illustrating an overall structure of the first embodiment.

The Figure 4 B ₃ pressure plate 103 is a view seen from the axial direction.

FIG. 5 is a view showing the structure and operation of a cam portion according to the first embodiment.

FIG. 6 is a view showing the structure and operation of a cam portion according to the first embodiment.

FIG. 7 is a diagram showing a structure of a cam portion according to the second embodiment.

FIG. 8 is a diagram illustrating a structure of a cam portion according to a third embodiment.

FIG. 9 is a diagram illustrating a structure of a cam portion according to a fourth embodiment.

FIG. 10 is a diagram illustrating an overall structure of a fifth embodiment.

FIG. 11 is a view showing the structure and operation of a cam portion according to a fifth embodiment.

FIG. 12 is a view showing the structure and operation of a cam portion according to a fifth embodiment.

FIG. 13 is a view showing the structure and operation of a cam portion according to a fifth embodiment.

[Explanation of symbols]

B ₃ ... third brake K ₂ ... rear planetary carrier 101 ... B ₃ housing 101a ... oil passage 102 ... B ₃ piston 103 ... B ₃ pressure plate 104 ... cam roller 105 ... initial spring 106 ... return spring 107 ... stopper 108 ... B ₃ clutch disks 109 ... connecting member 110 ... B ₃ separator plates 111 ... oil chamber C ₃ ... third clutch K ₃ ... OD planetary carrier 201 ... C ₃ housing 201a ... oil passage 202 ... C ₃ piston 203 ... C ₃ pressure plate 204 ... cam roller 205 ... spring 206 ... oil chamber 207 ... C ₃ clutch disks 208 ... connection members 210 ... C ₃ separator plate B ₄ ... fourth brake 301 ... B ₄ piston 302 ... B ₄ clutch disks 303 ... B ₄ separator plate 50 ... transmission case

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) F16D 13/00-13/76 F16D 25/00-25/14

Claims (3)

(57) [Claims] 1. A pair of cam members are disposed between a pair of members which are spaced apart from each other on a common axis and rotate relatively, and one of said pair of cam members relatively rotates one of said pair of cam members by initial movement means. A clutch device that presses against one of the members and relatively rotates in a predetermined direction to generate a cam force, and engages the relatively rotating member by the cam force, wherein the initial movement means does not use a fluid force. A clutch device, wherein one of the pair of cam members is pressed by a force. 2. The clutch device according to claim 1, wherein the mechanical force of the initial movement means is a biasing force of a spring member. 3. The clutch according to claim 1, wherein the mechanical force of the initial movement means is an inertial force obtained by moving one of the pair of cam members in the same state with respect to the other. apparatus.