JPH0634014A - Fluid transmission with lockup clutch - Google Patents

Abstract

(57) [Summary] [Purpose] To improve the effect of preventing muffled noise and to improve the control response of the lockup clutch. [Structure] A damper mass 12 to which a lockup clutch 11 is selectively engaged and which rotates together with a front cover 4.
A fluid transmission device with a lock-up clutch, comprising: a space portion 40 that exerts a hydraulic pressure that presses the lock-up clutch 11 toward the damper mass 12; and a hydraulic pressure that is supplied to this space portion 40 that acts and A hydraulic chamber 28 that presses the damper mass 12 toward the lockup clutch 11 by hydraulic pressure is provided. Further, the damper mass 12 is held so as to move toward the lockup clutch 11 by the hydraulic pressure supplied to the hydraulic chamber 28.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic power transmission device having a lockup clutch such as a torque converter in an automatic transmission for a vehicle.

[0002]

2. Description of the Related Art As is well known, a lockup clutch in a fluid transmission device such as a torque converter directly connects a member on the input side and a member on the output side by a mechanical means. A damper mechanism is also used to prevent vibration due to fluctuations in the. This type of damper mechanism is generally provided between a lockup clutch that selectively engages an input side member such as a front cover and an output side member such as a turbine hub. , The vibration damping characteristics were improved by incorporating a damper mass with a large inertial mass into the damper mechanism instead of such a structure and selectively engaging the lock-up clutch with the damper mass. The present applicant has already proposed a fluid transmission device by Japanese Patent Application No. 3-309835.

The structure thereof will be briefly described. The damper mechanism has an annular center plate as a driving member, and a damper spring is housed in a window hole formed in the center plate. The damper mass is composed of a main member having a large weight, and a cover member that sandwiches the center plate and the damper spring between the main member and the main member. It is designed to rotate relative to the plate. The damper mechanism is arranged between the front cover and the lockup clutch, and its center plate is connected and integrated with the housing at its outer peripheral portion. The lockup clutch is connected to the hub together with the turbine runner, and is engaged / disengaged with the damper mass by hydraulic pressure.

[0004]

In the above torque converter, the damper mechanism is positioned in the axial direction by fixing the center plate to the housing at its outer peripheral portion. A lockup clutch is arranged so as to face the damper mass in this damper mechanism, and a predetermined clearance is set between them.
However, the clearance of this lockup clutch is
It is necessary to set the size to a predetermined value or more in consideration of variations in machining accuracy and assembly accuracy of parts. Therefore, when engaging the lock-up clutch, the lock-up clutch moves between the clearances and is then pressed against the damper mass to transmit torque. Therefore, the stroke time until the lock-up clutch reaches the damper mass. Is the engagement delay time of the lockup clutch.

In the above-mentioned conventional device, since the stroke when the lockup clutch is engaged is long, the responsiveness of the control of the lockup clutch is not always good.
Therefore, for example, when a signal for engaging the lockup clutch is output based on the fact that the slip amount in the torque converter has become small, the slip amount in the torque converter is large when the lockup clutch is actually engaged. That is, the difference in rotation speed between the input-side member and the output-side member becomes large, and a shock may occur due to engagement of the lockup clutch.

On the other hand, although the damper mass is axially pressed by the lock-up clutch,
Since it is supported by the center plate via the damper spring, a reaction force means for pressing the damper mass in the direction of separating from the front cover when the lockup clutch is engaged is required. That is, if the damper mass comes into contact with the front cover, vibration may be transmitted between them and the muffled sound may become loud. Therefore, if a bearing such as a thrust bearing is used as this type of reaction force means, not only the number of parts increases,
Since these bearings also transmit the vibration, there is a disadvantage that the muffled noise becomes loud.

The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to improve control response of a lockup clutch in a hydraulic power transmission device and prevent an increase in muffled noise without increasing the number of parts. It is what

[0008]

In order to achieve the above object, the present invention provides an input member integrated with a pump impeller, an output member integrated with a turbine runner, and a lock that rotates together with the output member. In a fluid transmission device with a lock-up clutch, comprising an up-clutch and an engaged member which is selectively engaged by the lock-up clutch and rotates together with the input member, the lock-up clutch is directed toward the engaged member. A first hydraulic chamber for applying a pressing hydraulic pressure; and a second hydraulic chamber for operating the hydraulic pressure supplied to the first hydraulic chamber and pressing the engaged member toward the lockup clutch by the hydraulic pressure. It is characterized by that.

Further, according to the present invention, the engaged member may be held so as to move toward the lock-up clutch by the hydraulic pressure supplied to the second hydraulic chamber.

[0010]

The lockup clutch of the fluid transmission according to the present invention rotates together with the output member, and the engaged member engaged with the lockup clutch rotates together with the input member. When the hydraulic pressure is supplied to the first hydraulic chamber, the lockup clutch is pressed by the hydraulic pressure toward the engaged member. On the other hand, since the same hydraulic pressure is supplied to the second hydraulic chamber, a force that pushes the engaged member toward the lockup clutch acts on the engaged member. Therefore, when the lockup clutch is engaged, the oil pressure in the second hydraulic chamber acts so as to cancel the force pressing the engaged member by the lockup clutch, and the engaged member is held at the desired position. .

When the engaged member can move toward the lockup clutch, the hydraulic pressure is supplied to the first hydraulic chamber to engage the lockup clutch, and at the same time, the same hydraulic pressure acts on the second hydraulic chamber. The lockup clutch moves toward the engaged member, and the engaged member moves toward the lockup clutch. Therefore, these two approaches each other and the lock-up clutch is engaged, so that the responsiveness is improved. When releasing the lock-up clutch, the lock-up clutch and the engaged member move in the directions away from each other.
The time required to release the lockup clutch is shortened,
Responsiveness is improved.

[0012]

Embodiments of the present invention will now be described with reference to the drawings. FIG. 1 is a sectional view showing an embodiment of the present invention, in which a shell 2 of a pump impeller 1 is integrally connected to a front cover 4 via an annular extension member 3. The extension member 3 and the front cover 4 form a torque converter housing 5. Inside the housing 5, a turbine runner 6 is arranged so as to face the pump impeller 1.
The turbine runner 6 is attached at its inner peripheral portion to a hub 7 which is an output member by rivets 8. Further, between the pump impeller 1 and the turbine runner 6, and on the inner peripheral side thereof, a stator 10 spline-fitted to the outer race of the one-way clutch 9 is arranged. And the inner surface of the front cover 4 and the turbine runner 6
A lock-up clutch 11 and a damper mechanism 13 including a damper mass 12, which is a rotary inertia mass body, are arranged between and.

The lock-up clutch 11 is a lock-up piston 14 which is an annular plate member curved along the back surface (left side surface in FIG. 1) of the turbine runner 6 and a lining material attached to the outer peripheral side surface thereof. It is composed of 15 and. A cylindrical portion 16 is formed on the inner peripheral portion of the lock-up piston 14, and the cylindrical portion 16 is formed.
A plurality of protrusions 17 acting as engaging teeth for torque transmission are formed at one end portion (left end portion in FIG. 1) of the disk so as to be spaced at regular intervals in the circumferential direction and project toward the inner peripheral side. Has been done.

The lock-up piston 14 is the hub 7
Is fitted so as to be slidable in the axial direction. This hub 7
Has a boss portion 18 into which the cylindrical portion 16 of the lockup piston 14 is fitted, and a seal ring 19 attached thereto seals the lockup piston 14 and the lockup piston 14 in a liquid-tight state. . Also this boss 1
A plurality of protrusions 20 that engage with the protrusions 17 in the circumferential direction are formed on one side surface (the left side surface in FIG. 1) of 8.
Therefore, torque is transmitted between the lock-up piston 14 and the hub 7 by the protrusion 17 and the protrusion 20.

The damper mass 12 has a main member 21 having an outer diameter substantially equal to that of the lock-up piston 14 and an inner diameter smaller than that of the lock-up piston 14 and having a substantially annular shape as a whole, and having a larger inner diameter and smaller mass. It is composed of an annular cover member 22. The main member 21 and the cover member 22 are connected to each other by rivets 23 so as to face each other to form the damper mass 12, and are arranged between the lockup piston 14 and the inner surface of the front cover 4. This damper mass 12
The inner peripheral portion of the main member 21 is rotatably fitted to the outer peripheral surface of the annular protrusion 24 provided on the inner surface of the front cover 4 so as to be positioned on the same axis as the housing 5. That is, it is centered with respect to the housing 5.

Further, on the main member 21, an annular projection 25 having the same inner diameter as that of the cylindrical portion 16 of the lockup piston 14 is formed toward the inner surface of the front cover 4. The annular protrusion 25 is rotatably fitted to a boss portion 26 protruding from the inner surface of the front cover 4. A space between the annular projection 25 and the boss portion 26 is liquid-tightly sealed by a seal ring 27 attached to the boss portion 26. That is, the radius R14 of the seal portion on the inner peripheral side of the lock-up piston 14 and the radius R12 of the seal portion on the inner peripheral side of the damper mass 12 are made equal.
By sealing the space between the front cover 4 and the damper mass 12 with a seal ring 27 in a liquid-tight state,
A hydraulic chamber 28 is formed between the inner surface of the front cover 4 and the damper mass 12.

Main member 2 forming damper mass 12
In each of the facing portions of 1 and the cover member 22, a plurality of concave portions along the circumferential direction are formed at regular intervals, and a damper spring 29 which is a coil spring is accommodated therein. A center plate 30 which is an annular plate-shaped member is provided between the main member 21 and the cover member 22.
However, they are sandwiched so as to be rotatable relative to the damper mass 12. Further, the center plate 30 is formed with a window hole into which the damper spring 29 is fitted. Therefore, when the damper mass 12 and the center plate 30 rotate relatively, the damper mass 12 and the center plate 30 compress the damper spring 29.

Further, the outer peripheral portion of the center plate 30 is
The housing 5 is engaged with the housing 5 in the circumferential direction, and torque is transmitted between the two. Further, between the outer peripheral portion of the center plate 30 and the meshing portion of the housing 5, as shown in an enlarged view in FIG. 2, predetermined clearances (clearances) C1 and C2 are set in the axial direction,
It is configured to be movable in the axial direction. Further, as the meshing structure, various structures can be adopted as required. For example, the outer peripheral end of the front cover 4 is formed with teeth protruding in the axial direction, and the outer periphery of the center plate 30 is formed. It is also possible to form teeth projecting outward in the radial direction at the ends and engage these teeth to transmit torque between the housing 5 and the center plate 30.

Reference numeral 31 in FIG. 1 is a friction plate, and the friction plate 31 is an annular member as a whole in which elastically deforming arcuate cross-sections 32 are formed at regular intervals. The friction plate 31 is positioned such that its arcuate section 32 has a predetermined play in the circumferential direction inside a punched portion formed in the cover member 22 at predetermined intervals in the circumferential direction. Thus, it is arranged on the inner surface side of the front cover 4.
The bow-shaped cross section 32 is elastically deformed and sandwiched between the front cover 4 and the center plate 30,
Due to the elastic force, the bow-shaped cross section 32 causes the front cover 4
It is strongly pressed against the inner surface of the center plate 30 and the center plate 30. Further, a friction material (not shown) is provided on the surface of the friction plate 31 facing the inner surface of the front cover 4.
Is attached.

The above-described torque converter transmits the torque by applying the fluid flow generated by the pump impeller 1, that is, the spiral flow of oil to the turbine runner 6 to rotate the turbine runner 6, and therefore the housing 5 The inside of the is filled with oil. Further, the lockup clutch 11 is a clutch that engages / disengages in accordance with a pressure difference between both sides of the lockup piston 14, and therefore, the space portion on the turbine runner 6 side with respect to the lockup piston 14 ( That is, the oil passage (FIG. 1) for supplying hydraulic pressure to the first hydraulic chamber 40 in the present invention.
An oil passage indicated by an arrow A) and an oil passage supplying an oil pressure between the lockup piston 14 and the damper mass 12 (an oil passage indicated by an arrow B in FIG. 1).

As is known from the configuration shown in FIG.
When the lock-up piston 14 moves to the left in FIG. 1 and the lining material 15 comes into contact with the damper mass 12 so that torque can be transmitted, that is, when the lock-up clutch 11 is engaged, the hydraulic chamber 28 is locked with the damper mass 12. Although not in communication with the up piston 14, it communicates with the space portion 40 to which hydraulic pressure is supplied from the lock up piston 14 toward the turbine runner 6 side, that is, in the direction of arrow A. In other words, the hydraulic pressure for engaging the lockup clutch 11 also acts on the hydraulic chamber 28. Therefore, this hydraulic chamber 28 is the second hydraulic chamber in the present invention.

Next, the operation of the torque converter shown in FIG. 1 will be described. FIG. 1 shows a lock-up / off state, that is, a state in which the lock-up clutch 11 is released. Supplying hydraulic pressure from the direction of arrow B to increase the hydraulic pressure between the lock-up piston 14 and the damper mass 12. As a result, the lockup piston 14 is separated from the damper mass 12. When torque is applied to the front cover 4 from an engine (not shown) in this state, the pump impeller 1 rotates together with the housing 5 to generate a spiral flow of oil. By giving the spiral flow to the turbine runner 6, torque is transmitted to the turbine runner 6 and rotates together with the hub 7. The torque is transmitted to the automatic transmission via an input shaft (not shown) fitted to the hub 7.

On the other hand, since the damper mass 12 is connected to the housing 5 by the damper mechanism 13 including the center plate 30 and the damper spring 29, it rotates integrally with the housing 5. In that case, since the main member 21 of the damper mass 12 is fitted to the annular projection 24 of the front cover 4 and the damper mass 12 is positioned on the same axis as the front cover 4, the damper mass 12 is rotated. Does not vibrate or make noise. Further, since the damper mass 12 has a large inertial mass due to an increase in weight, an inertial resistance is generated with respect to the fluctuation of the input torque, and the vibration caused by the fluctuation of the input torque is damped or controlled.

When the lockup clutch 11 is engaged, that is, when the lockup is turned on, the lockup clutch 11 shown in FIG.
The hydraulic pressure is supplied in the direction of arrow A and is discharged in the direction opposite to arrow B. In that case, the lining material 15
Since the distance between the main member 21 and the main member 21 is small, the orifice effect of this portion causes the lockup piston 14 and the main member 2
1, the pressure in the space between the lockup piston 1 and the rear side of the lockup piston 14, that is, the lockup piston 1
4, the pressure in the space 40 on the turbine runner 6 side becomes higher. As a result, the lockup piston 14 moves toward the damper mass 12.

When the pressure receiving area of the lockup piston 14 is S, the supply pressure is Pa, and the drain pressure is Pb, a pressing force of Fp = S | Pa-Pb | acts on the lockup piston 14, and Lockup piston 1
The moving speed Vp of No. 4 is Vp = (Fp / Mp) t (Mp: mass of lockup piston, t: time).

On the other hand, the hydraulic chamber 28 is sealed by a seal ring 27 in a liquid-tight state with respect to a low pressure portion between the damper mass 12 and the lockup piston 14.
Further, since the high pressure portion on the turbine runner 6 side is communicated with, the pressure in the hydraulic chamber 28 is equal to that of the lockup piston 1.
4 becomes equal to the pressure for pressing the damper mass 12 side.
The radius R of the seal portion on the inner peripheral side that divides the hydraulic chamber 28
Since 12 and the radius R14 of the seal portion on the inner peripheral side of the lockup piston 14 are equal, a load equal to the load for pushing the lockup piston 14 acts on the damper mass 12.
The entire damper mechanism 13 moves to the lockup piston 14 side.

A pressing force of Fd = S | Pa-Pb | acts on the damper mass 12. Since the elastic force of the friction plate 30 acts on the damper mechanism 13 in the axial direction, if the elastic force is Ff, the damper mechanism 1 will be described.
The moving speed Vd of 3 is Vd = {(Fp + Ff) / Md} t (Md: mass of damper mechanism).

By thus supplying the hydraulic pressure in the direction of arrow A in FIG. 1 and exhausting the hydraulic pressure in the direction opposite to the direction of arrow B, the lockup piston 14 and the damper mechanism 13 both approach each other at a predetermined speed. Then, the two come into contact with each other so as to transmit torque. Conventionally, since the damper mechanism 13 is fixed in the axial direction, the above-mentioned Vd = 0, and as is apparent from comparison with this, in the above torque converter,
Even if the stroke required to engage the lockup clutch 11 is long, the time required to engage the lockup clutch 11 is shortened by the speed component of Vd described above, and the responsiveness thereof is improved.

When the lock-up clutch 11 is engaged, the load for pushing the lock-up piston 14 leftward in FIG. 1 and the load for pushing the damper mass 12 rightward in FIG. The mass 12 is kept at a position away from the inner surface of the front cover 4. Therefore, the input torque transmitted to the front cover 4 is transmitted to the damper mass 12 via the damper spring 29 in the damper mechanism 13, and further the damper mass 1 is transmitted.
2 is transmitted to the lockup piston 14. That is, the housing 5 and the center plate 30 that rotates integrally with the housing 5 serve as an input member, and the damper mass 12
Is the engaged member.

When the input torque fluctuates, the damper mass 12 is rotatable with respect to the housing 5, and the lock-up piston 14 is in contact with the damper mass 12 so that the torque can be transmitted. 1
Members such as 2 and the lock-up piston 14 act as inertial resistance. As a result, the damper spring 29 is compressed according to the fluctuation of the input torque, and the damper spring 2
9 absorbs the vibration.

Further, in the structure shown in FIG. 1, when the energy stored in the damper spring 29 is released, the friction plate 31 makes a large sliding movement between the damper mass 12 of the damper mechanism 13 and the inner surface of the front cover 4. Due to the resistance, a part of the emitted energy is absorbed in the sliding part. That is, when the relative rotation between the damper mass 12 and the drive-side member such as the center plate 31 increases as the input torque fluctuates greatly, the arcuate cross section 32 of the friction plate 31.
A clearance (play) in the circumferential direction between the cover member 22 and the punched portion of the cover member 22 disappears, the friction plate 31 and the damper mass 12 rotate integrally, and the friction plate 31 slides with respect to the front cover 4. . The sliding resistance at that time acts so as to suppress the relative rotation of the damper mass 12, and as a result, the "hiccuping" phenomenon, which is a long variation in the wavelength of the output shaft torque, is prevented, and the riding comfort is improved. Further, when the input torque is small or when the fluctuation of the input torque is small, there is a gap in the circumferential direction between the arcuate cross section 32 of the friction plate 31 and the punched portion of the cover member 22, and the friction plate 31 is Since the damper mass 12 and other members on the output side do not come into contact with each other, adverse effects such as loud muffled noise do not occur.

On the other hand, when the lockup clutch 11 is released, the hydraulic pressure is supplied in the direction of arrow B in FIG. 1 and the pressure is discharged in the direction opposite to the direction of arrow A. If the supply and discharge states of the hydraulic pressure are changed in this way, the hydraulic pressure inside the space 40 on the back side of the lock-up piston 14 that is the first hydraulic chamber and the hydraulic pressure inside the hydraulic chamber 28 that is the second hydraulic chamber will be Since the hydraulic pressure in the portion between the mechanism 13 and the lockup piston 14 becomes lower, the lockup piston 14 retracts to the right in FIG. 1 and the damper mechanism 13 retracts to the left in FIG. That is, since the lock-up piston 14 and the damper mass 12 that have been in contact with each other move simultaneously in the directions away from each other, the lock-up clutch 11 is quickly released and its responsiveness is improved. That is, the response speed when the lockup clutch 11 is released is faster than the conventional one by the speed component of the moving speed Vd = {(Fp-Ff) / Md} t of the damper mechanism 13.

Next, another embodiment of the present invention will be described. In the example shown in FIG. 3, instead of the extension member 3 shown in FIG. 1, a ring-shaped intermediate member 50 having a positioning protrusion 49 protruding in the axial direction is provided between the shell 2 of the pump impeller 1 and the front cover 4. Intervening in.
Further, an engagement portion 30a bent toward the positioning projection 49 is formed on the outer peripheral portion of the center plate 30, and the engagement portion 30a engages with the housing 5 in the rotational direction and the engagement thereof. Predetermined gaps C1 and C2 are set on both front and rear sides in the axial direction of the portion 30a, that is, between the positioning projection 49 and the inner surface of the front cover 4, as shown in an enlarged view in FIG. ing. Therefore, the damper mechanism 13 has the clearances C1 and C2.
It is possible to move in the axial direction only by the dimension according to. Further, in the example shown in FIG. 3, the friction plate 31 is not provided. Other configurations are the same as the configurations shown in FIG.

Therefore, also in the torque converter shown in FIG. 3, when hydraulic pressure is supplied to engage the lockup clutch 11, the lockup piston 14 and the damper mechanism 13 move so as to approach each other, and the lockup occurs. When the hydraulic pressure is supplied to release the clutch 11, the lockup piston 14 and the damper mechanism 13 move in the directions in which they are separated from each other, so that the control response of the lockup clutch 11 is improved. The torque converter shown in FIG. 3 can also provide the same vibration damping characteristics and muffled sound prevention effect as those of the example shown in FIG.

In the example shown in FIG. 5, the lockup piston 1 is used.
By sandwiching 4 with two types of damper masses, the engaging force of the lock-up clutch 11 is increased. In the following description, the same components as those shown in FIG. 1 will be assigned the same reference numerals as those in FIG. 1 and will not be described.

In FIG. 5, the shell 2 of the pump impeller 1 is welded to and integrated with the front cover 4, and the shell 2 and the front cover 4 form a torque converter housing 5. The first damper mass 68 is arranged along the inner surface of the front cover 4,
The first damper mass 68 has a cylindrical portion 69 extending in the axial direction at the outer peripheral end, and the annular protrusion 58 provided near the center of the front cover 4 has a bush 7 attached thereto.
It is rotatably fitted through 0, and the position in the radial direction is determined by this bush 70. Therefore, the first damper mass 68 is configured to be movable in the axial direction.

Another annular projection 57 is formed on the inner surface of the front cover 4 near the outer circumference. The first damper mass 68 fits into the annular projection 57 and is sealed by the seal ring 62. ing. Further, an annular second damper mass 71 having a substantially triangular cross section or a substantially trapezoidal cross section is spline fitted to the inner peripheral surface of the cylindrical portion 69 so as to be movable in the axial direction, and is sealed by the seal ring 65. There is.

The lock-up piston 14 is inserted between the damper masses 68 and 71, and the lining material 15 is attached to both front and back surfaces thereof. The lining material 15 on the side of the first damper mass 68 is provided with a groove (not shown) extending from the inner peripheral end to the outer peripheral end thereof.

Lockup piston 14 of the example shown in FIG.
Are connected to the hub 7 via an intermediate member 72. The intermediate member 72 is fixed to the hub 7 along with the turbine runner 6 at its inner peripheral portion, and a cylindrical portion 73 having an outer diameter substantially equal to the inner diameter of the annular protrusion 57 near the outer periphery of the front cover 4 is formed on the outer peripheral portion thereof. Has been done. The lockup piston 14 is fitted in the cylindrical portion 73 so as to be movable in the axial direction, and is sealed by an O-ring 74. Therefore, the inner diameter of the hydraulic chamber 28 between the inner surface of the front cover 4 and the first damper mass 68 is substantially equal to the inner diameter of the pressure receiving surface of the lockup piston 14. Further, the lock-up piston 14 and the intermediate member 72 are coupled to each other by a convex / concave portion 75 formed so as to mesh with each other in the circumferential direction so that torque can be transmitted.

A plurality of pairs of protrusions 60 are formed on the inner surface of the front cover 4 between the annular protrusions 57 and 58 at regular intervals in the circumferential direction. Tamper spring 2 held by 68
9 are arranged between each pair of protrusions 60. Therefore, when the damper mass 68 rotates relative to the front cover 4, the damper spring 29 is compressed between the protrusion 60 and the damper mass 68.

Therefore, also in the torque converter shown in FIG. 5, the space 40 in the housing 5 in which the turbine runan 6 is housed is the first hydraulic chamber, and the first damper mass 68 and the front cover 4 are also provided. The hydraulic chamber 28 between is the second hydraulic chamber.

If the hydraulic pressure is supplied in the direction of arrow A in FIG. 5, the hydraulic pressure inside the space 40 and the hydraulic chamber 28 will be the hydraulic pressure between the intermediate member 72 and the first damper mass 68 and at the place communicating therewith. As it goes higher, the lockup piston 14 and the first damper mass 68 move toward each other, resulting in quick engagement. At the same time, the second damper mass 71 locks up the piston 1.
4 is moved so as to be sandwiched between the first damper mass 68 and the first damper mass 68. Further, if the hydraulic pressure is supplied in the opposite direction, the first damper mass 68 and the lockup piston 14 move in the directions away from each other, so that the lockup clutch 11 is quickly released.

Therefore, even with the configuration shown in FIG. 5, when the lockup clutch 11 is engaged and released, the lockup piston 14 and the damper masses 68, 71 move in a direction in which they approach or separate from each other. The control response of the up clutch 11 can be improved.

The present invention is not limited to the above embodiments, and other than the above torque converter,
It can also be applied to fluid couplings that do not have a torque amplification effect.

[0045]

As described above, in the present invention, by supplying the hydraulic pressure for engaging the lockup clutch, it is possible to apply a pressure against the pressing force of the lockup clutch to the engaged member. Since the hydraulic chamber is formed, without using supporting members such as bearings,
The engaged member can be held at a desired position such as a position where it does not come into contact with the input member. Therefore, transmission of vibration to the lockup clutch via the engaged member can be performed without increasing the number of parts. It can be avoided and the muffled sound can be prevented from being deteriorated.

Further, the engaged member with which the lock-up clutch engages can be moved toward and away from the lock-up clutch, so that the engaged force is exerted by the hydraulic pressure acting on the hydraulic chamber when the lock-up clutch is engaged. Since the member moves toward the lockup clutch, it is possible to shorten the time required to engage the lockup clutch and improve the control response thereof.

[Brief description of drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention.

FIG. 2 is an enlarged partial sectional view showing an engaging portion between the center plate and the housing.

FIG. 3 is a partial sectional view showing another embodiment of the present invention.

4 is an enlarged partial cross-sectional view showing an engaging portion between a center plate and a housing in the example shown in FIG.

FIG. 5 is a partial cross-sectional view showing still another embodiment of the present invention.

[Explanation of symbols]

 1 Pump Impeller 4 Front Cover 6 Turbine Runner 7 Hub 11 Lockup Clutch 12 Damper Mass 28 (To be the 2nd Hydraulic Chamber) Hydraulic Chamber 40 (To Be the 1st Hydraulic Chamber) Space Section

Claims (2)

[Claims] 1. An input member integrated with a pump impeller, an output member integrated with a turbine runner, a lockup clutch rotating with the output member, and an input member with which the lockup clutch is selectively engaged. In a fluid transmission device with a lock-up clutch, which includes an engaged member that rotates together with the engaged member, a first hydraulic chamber that applies a hydraulic pressure that presses the lock-up clutch toward the engaged member, and the first hydraulic chamber. And a second hydraulic chamber that presses the engaged member toward the lock-up clutch by the hydraulic pressure supplied to the lock-up clutch. 2. The lockup according to claim 1, wherein the engaged member is held so as to move toward the lockup clutch by hydraulic pressure supplied to the second hydraulic chamber. Fluid transmission with clutch.