JP2836386B2 - Fluid transmission with lock-up clutch - Google Patents

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 having a lock-up 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 torque converter transmits torque by supplying a spiral flow of fluid generated by a pump impeller to a turbine runner and rotating the turbine runner. Therefore, since the fluid mediates the transmission of torque, vibration and noise caused by torque fluctuation of the engine can be absorbed to some extent. Conventionally, lock-up clutches have been frequently used to improve the power transmission efficiency of a torque converter. Since the lock-up clutch directly connects the input side member and the output side member of the torque converter by mechanical means, if the lock-up clutch is engaged, the lock-up clutch may cause a change in engine torque. The transmitted vibration is transmitted to the automatic transmission or the output shaft as it is, and the ride comfort may be degraded.

For this purpose, a damper mechanism is generally used in combination with a lock-up clutch. As an example, Japanese Patent Application Laid-Open No. 63-251664 discloses an annular weight connected to a front cover via a damper mechanism. A torque converter is described in which a centrifugal clutch acting as a lock-up clutch is disposed on the inner peripheral side of an annular weight, and the centrifugal clutch is connected to a turbine runner.

According to the torque converter described in the above publication, the annular weight acts as an inertial mass for attenuating the vibration of the flywheel on the input side, and the damper mechanism is used during high-speed running when the centrifugal clutch is engaged. It is said that an inertial resistance is generated by the annular weight attached via the torsional vibration, thereby suppressing the generation of a muffled sound or the like caused by torsional vibration.

[0005]

The operating state in which the lock-up clutch is engaged, that is, the lock-up region, is preferably determined by a plurality of parameters such as the vehicle speed and the throttle opening. Set up area. Recently, in a specific driving state, the lock-up clutch is controlled to a slip state called half lock-up to improve fuel efficiency and ride comfort.

However, the above-mentioned centrifugal clutch that functions as a lock-up clutch engages and disengages according to the centrifugal force acting on it, so that it is difficult to reliably engage in a lock-up area assumed in advance. Conversely, there is a possibility that they will be engaged unnecessarily.

That is, since the centrifugal force acting on the centrifugal clutch changes only with the rotation speed of the turbine runner, in the above-described conventional torque converter, the lock-up clutch is controlled according to only one parameter. It is difficult to control the engagement / disengagement of the lock-up clutch according to the running state of the vehicle. Further, it is almost impossible to perform the half lock-up control only in a specific operation state. Further, since the rotation speed of the turbine runner frequently changes during traveling and greatly changes during gear shifting, a temporary increase in the turbine runner rotation speed during traveling or gear shifting causes the lock-up clutch to temporarily stop. And the resulting change in the output shaft torque may appear as a shock.

On the other hand, the centrifugal clutch needs to operate against the elastic force and sliding resistance of the return spring and generate a predetermined engaging force. Become. Therefore, in the above-described conventional torque converter in which the centrifugal clutch is a lock-up clutch, the mass on the turbine runner side is increased, so that the clutch synchronization energy at the time of shifting is increased, and the shift shock may be deteriorated.

The above-described conventional torque converter has advantages such as improvement of vibration damping characteristics and prevention of muffled sound by using an annular weight, but has a large disadvantage due to adoption of a centrifugal clutch as a lock-up clutch. However, it is considered difficult to put it into practical use. The centrifugal clutch, which is causing the inconvenience,
It is conceivable to replace the lockup clutch with a conventional general lock-up clutch which is disposed to face the inner surface of the front cover and is operated by hydraulic pressure.

However, since the above-described annular weight is supported in a so-called floating state by a spring of a damper mechanism, when the lock-up clutch is pressed against the annular weight to engage the lock-up clutch, the annular weight is not attached to the front cover. Will be pressed against the inner surface. As a result, torque is transmitted between the front cover and the annular weight due to the frictional force between the front cover and the annular weight, and the damping function of the damper mechanism is reduced accordingly. In other words, there is a problem that hysteresis due to frictional resistance increases and vibration damping characteristics deteriorate.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has as its object to provide a fluid transmission with a lock-up clutch which can improve vibration damping characteristics without impairing controllability. is there.

[0012]

SUMMARY OF THE INVENTION In order to achieve the above object, according to the present invention, a housing is formed by an outer shell of a pump impeller for generating a fluid flow and a front cover integrally connected to the outer shell. A turbine runner is disposed in the housing so as to face the pump impeller, and a lock-up clutch for selectively transmitting torque between the housing and an output member integrated with the turbine runner is provided in the housing. In the provided hydraulic power transmission with a lock-up clutch, a rotary inertia mass body rotatable relative to the housing is disposed between an inner surface of the front cover and the turbine runner and on the same axis as the housing. And an elastic body that is compressed when the rotary inertial mass body rotates relative to the housing. A damper mechanism is provided between the rotary inertial mass and the turbine runner. The damper mechanism is moved back and forth by fluid pressure in the axial direction of the housing so as to contact the rotary inertial mass so as to be capable of transmitting torque and transmit torque. A lock-up piston is disposed so as not to be spaced apart from the rotating inertial mass, and furthermore, when the lock-up piston comes into contact with the rotating inertial mass, a reaction force is applied to the rotating inertial mass toward the lock-up piston to front the rotating inertial mass. reaction force means are provided to maintain the cover inner surface in a non-contact state, and the rotational inertia lock-up piston across the lock-up piston when contacted to the rotating inertial mass
Space part on the mass body side and space part on the turbine runner side
And a sealing means for sealing the non-communication state.

Further, in the present invention, an annular projection protruding in the axial direction is formed on the inner surface of the front cover, and the rotary inertia mass is rotatably fitted to the annular projection, so that the rotary inertia mass is formed. Centering, that is, positioning on the same axis as the housing can be performed.

Further, according to the present invention, the lock-up piston can be used as a torque transmitting means.
The lock-up piston can be connected to an output member integral with the turbine runner so as to transmit torque.

In this invention, the fitting portion between the lock-up piston and the output member is made liquid-tight, and the radius from the rotation center to the fitting portion is provided on the inner peripheral side of the rotary inertial mass body. The radius of the sealed portion can be made substantially equal.

[0016]

According to the fluid transmission of the present invention, torque is transmitted between the pump impeller and the turbine runner via the fluid. If the lock-up piston is in contact with the rotating inertial mass so as to be able to transmit torque, a part of the input torque is transmitted to the output member without passing through the fluid. Since the rotating inertial mass is connected to the housing via the damper mechanism, regardless of the operation of the lock-up piston, it generates an inertial resistance to the input torque, and as a result, due to the fluctuation of the input torque. Suppress vibration.

Further, when the lock-up piston is in contact with the rotary inertial mass so as to transmit torque, it absorbs vibrations caused by fluctuations in the input torque, and reduces or suppresses muffled noise and the like. Since the lock-up piston can be brought into contact with and separated from the rotary inertial mass body by hydraulic pressure, engagement / disengagement of the lock-up clutch can be arbitrarily controlled, thereby improving controllability. Also, when the lock-up piston is pressed against the rotating inertial mass body by hydraulic pressure, a reaction force opposing the pressing force acts on the rotating inertial mass body by the reaction force means, so that the rotating inertial mass body comes into frictional contact with the front cover. There is no. Therefore, even when the lock-up clutch is engaged, free rotation of the rotating inertial mass body with respect to the housing is possible, so that a favorable vibration damping characteristic can be maintained.

Further, a space on the rotating inertial mass body side with the lock-up piston interposed therebetween by a sealing means and the taper.
-Since the space part on the bin runner side can be made in a non-communication state, leakage of fluid pressure that presses the lock-up piston against the rotating inertial mass body is prevented, and the lock-up piston rotates reliably or at an arbitrary controlled pressure. The inertial mass can be contacted. And in this invention,
The weight required for vibration damping is secured by the rotating inertial mass body, and the lock-up piston, which is the output side member, can be made lightweight, so that the clutch synchronization energy during shifting is reduced and shift shock is reduced. This is advantageous.

Further, since the rotary inertia mass body is a heavy member, if the rotary inertia mass body is positioned and centered at the boss portion of the front cover, the axes of the two coincide with each other. As a result, vibration and noise may occur during rotation. Is reduced.

Further, if the lock-up piston is non-rotatably connected to the output member, the lock-up piston also serves as a transmission member, so that the number of parts can be reduced and the size and weight can be reduced.

On the other hand, the radius from the rotation center of the seal portion sealing the rotary inertia mass body on the inner peripheral side thereof and the radius from the rotation center of the seal portion sealing the lock-up piston on the inner peripheral side thereof are described. By making the radius approximately equal, the forces acting in the axial direction across the rotating inertial mass and the lock-up piston are almost balanced, preventing the rotating inertial mass and the lock-up piston from moving in the axial direction can do.

[0022]

Next, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a sectional view showing an embodiment of the present invention. 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. A turbine runner 6 is disposed inside the housing 5 so as to face the pump impeller 1.
The turbine runner 6 is attached to a hub 7 serving as an output member by a rivet 8 at an inner peripheral portion thereof. Further, between the pump impeller 1 and the turbine runner 6 and on the inner peripheral side thereof, a stator 10 spline-fitted to an outer race of the one-way clutch 9 is disposed. The inner surface of the front cover 4 and the turbine runner 6
Between the lock-up clutch 11, the damper mass 12 which is a rotary inertia mass body, and the damper mechanism 13
Is arranged.

The lock-up clutch 11 includes a lock-up piston 14 which is an annular plate-like member curved along the rear surface (the left side surface in FIG. 1) of the turbine runner 6 and a lining material attached to the outer peripheral side surface thereof. 15. FIG. 2 shows the lock-up piston 14. A cylindrical portion 16 is formed on the inner peripheral portion of the lock-up piston 14, and one end of the cylindrical portion 16 (the left end portion of FIG. ), A plurality of projections 17 acting as engagement teeth for transmitting torque are formed at regular intervals in the circumferential direction and protrude inward.

The lock-up piston 14 is connected to the hub 7
Are slidably fitted in the axial direction. This hub 7
As shown in FIG. 3, the boss 18 has a boss portion 18 for fitting the cylindrical portion 16 of the lock-up piston 14, and the seal ring 19 attached thereto has a liquid-tight state between the lock-up piston 14 and the lock-up piston 14. It is designed to be sealed. A plurality of protrusions 20 are formed on one side surface (left side surface of FIG. 3B) of the boss portion 18 to engage with the protrusions 17 in the circumferential direction. Therefore, the projection 17 and the projection 20 allow the lock-up piston 14
And the hub 7 transmits torque.

The damper mass 12 has a substantially annular main member 21 having an outer diameter substantially equal to the lock-up piston 14 and an inner diameter smaller than the lock-up piston 14, and a larger inner diameter and a smaller mass. And 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 disposed between the lock-up piston 14 and the inner surface of the front cover 4. This damper mass 12
Is positioned on the same axis as the housing 5 by rotatably fitting an inner peripheral portion of the main member 21 to an outer peripheral surface of an annular projection 24 projecting from an inner surface of the front cover 4. That is, it is centered with respect to the housing 5.

An annular projection 25 having the same inner diameter as the cylindrical portion 16 of the lock-up piston 14 is formed on the main member 21 toward the inner surface of the front cover 4. The annular projection 25 is rotatably fitted to a cylindrical portion 26 projecting from the inner surface of the front cover 4. The space between the annular projection 25 and the cylindrical portion 26 is sealed in a liquid-tight state by a seal ring 27 attached to the cylindrical portion 26. That is, the radius R14 of the seal portion on the inner peripheral side of the lock-up piston 14 and the damper mass 12
Are configured so that the radius R12 of the seal portion on the inner peripheral side is equal. And front cover 4 and damper mass 1
2 between the inner surface of the front cover 4 and the damper mass 1 by sealing in a liquid-tight state with a seal ring 27.
2, a hydraulic chamber 28 is formed.

Main member 2 forming damper mass 12
A plurality of concave portions along the circumferential direction are formed at regular intervals in each of the opposing portions of the cover member 1 and the cover member 22, and a damper spring 29, which is a coil spring, is housed therein. Between the main member 21 and the cover member 22, a center plate 30 which is an annular plate-like member is provided.
Are sandwiched so as to be rotatable relative to the damper mass 12. The center plate 30 has a window hole in which the damper spring 29 is fitted. Therefore, when the damper mass 12 and the center plate 30 rotate relatively, the damper spring 29 is compressed by the damper mass 12 and the center plate 30.

Further, the outer peripheral portion of the center plate 30
The housing 5 is engaged with the housing 5 in the circumferential direction, so that torque is transmitted between the two. As the meshing structure, various structures can be adopted as necessary. For example, teeth protruding in the axial direction are formed at the outer peripheral end of the front cover 4 described above, and the outer peripheral end of the center plate 30 is formed. The teeth may be formed so as to protrude outward in the radial direction, and the teeth may be engaged to transmit torque between the housing 5 and the center plate 30.

In FIG. 1, reference numeral 31 denotes a friction plate. The friction plate 31 is a member having a ring shape as a whole in which arcuate cross sections 32 which are elastically deformed are formed at regular intervals. The friction plate 31 is disposed on the inner surface side of the front cover 4 such that the arcuate cross section 32 is located at a predetermined gap in the circumferential direction at the punched portion of the cover member 22. The arcuate cross section 32 is elastically deformed and sandwiched between the front cover 4 and the center plate 30, and the elastic force causes the arcuate cross section 32 to strongly adhere to the inner surface of the front cover 4 and the center plate 30. It is imposed.

The torque converter described above transmits a torque by supplying a fluid flow, that is, a spiral flow of oil, generated by the pump impeller 1 to the turbine runner 6 and rotating the turbine runner 6. The interior is filled with oil. The lock-up clutch 11 is a clutch that engages and disengages in accordance with a pressure difference between both sides of the lock-up piston 14. Therefore, the lock-up clutch 11 is provided in a space on the turbine runner 6 side with respect to the lock-up piston 14. An oil passage for supplying oil pressure (oil passage indicated by arrow A in FIG. 1) and an oil passage for supplying oil pressure between lock-up piston 14 and damper mass 12 (oil passage indicated by arrow B in FIG. 1) Is formed.

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 as to transmit torque, that is, when the lock-up clutch 11 is engaged, the hydraulic chamber 28 locks with the damper mass 12. Although there is no communication between the lock-up piston 14 and the lock-up piston 14, the lock-up piston 14 communicates with the turbine runner 6, that is, at a location where hydraulic pressure is supplied in the direction of arrow A. In other words, the hydraulic pressure for engaging the lock-up clutch 11 also acts on the hydraulic chamber 28.

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, in which a hydraulic pressure is supplied 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 lock-up 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. When the spiral flow is given to the turbine runner 6, torque is transmitted to the turbine runner 6 and rotates 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, the damper mass 12 rotates integrally with the housing 5. In this case, the damper mass 12 has its main member 21 fitted into 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. Does not vibrate or generate abnormal noise. Further, since the inertia mass of the damper mass 12 is increased by increasing the 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 attenuated or controlled.

When the lock-up clutch 11 is engaged, that is, when the lock-up clutch is turned on, FIG.
And supplies the oil pressure in the direction opposite to the arrow B. The lining material 15 and the main member 2
1, the pressure in the space between the lock-up piston 14 and the main member 21 decreases due to the orifice effect of this portion, and the lock-up piston 1
The pressure in the space on the back side of 4, that is, in the space on the turbine runner 6 side from the lock-up piston 14 becomes higher. As a result, the lock-up piston 14 relatively approaches the damper mass 12 and the lining material 15 comes into contact with the side surface of the main member 21 so as to transmit torque.

In this case, the hydraulic chamber 28 is
The damper mass 12 and the lock-up piston 1
The pressure in the hydraulic chamber 28 causes the lock-up piston 14 to move the lock-up piston 14 Side pressure. Since the radius R12 of the seal portion on the inner peripheral side defining the hydraulic chamber 28 is equal to the radius R14 of the seal portion on the inner peripheral side of the lock-up piston 14, the lock-up piston 14
1 and the load pressing the damper mass 12 rightward in FIG. 1 are balanced, and the damper 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 of the damper mechanism 13 and further transmitted from the damper mass 12 to the lock-up piston 14.
Is transmitted to 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 as to transmit torque.
2 and a member such as the lock-up piston 14 act as inertial resistance. As a result, the damper spring 29 is compressed according to the change in the input torque, and the damper spring 2
9 absorbs vibration.

The lock-up piston 14 has a projection 17 formed on the inner peripheral portion thereof circumferentially engaged with a projection 20 formed on the side surface of the hub 7 as an output member. Lock-up piston 1 from 12
4 is transmitted to the projection 17 and the projection 20.
Through the hub 7. That is, in the configuration shown in FIG.
And a transmission member for transmitting torque from the damper mass 12 to the hub 7.

In the configuration shown in FIG. 1, when the energy stored in the damper spring 29 is released, the friction plate 31 slides more between the damper mass 12 of the damper mechanism 13 and the inner surface of the front cover 4. Because of the resistance, a part of the emitted energy is absorbed by the sliding part. That is, when the relative rotation between the damper mass 12 and the driving-side member such as the center plate 31 increases due to the large fluctuation of the input torque, the arcuate cross-section 32 of the friction plate 31
There is no gap in the circumferential direction between the punching portion of the cover member 22 and 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 "hiccup" phenomenon, which is a long fluctuation of the wavelength of the output shaft torque, is prevented, and the riding comfort is improved. When the input torque is small and the fluctuation of the input torque is small, there is a circumferential gap between the arcuate section 32 of the friction plate 31 and the punched portion of the cover member 22, and the friction plate 31 Since it does not come into contact with members on the output side such as the damper mass 12, there is no adverse effect such as a loud noise.

As described above, since the mass required for the damper mechanism 13 is ensured by the damper mass 12, the lock-up piston 14 can be reduced in weight, so that the lock-up clutch 11 can be released during shifting. For example, the amount of energy to be absorbed by the clutch of the automatic transmission during shifting is reduced, which is advantageous in reducing shift shock.

Next, another embodiment of the present invention will be described. The example shown in FIG. 4 uses a thrust bearing 40 as a reaction force means for holding the damper mass 12 at a position separated from the inner surface of the front cover 4, and accordingly, the sealing means is different from the structure shown in FIG. Further, the friction plate 31 is eliminated.

That is, in the torque converter shown in FIG. 4, the housing 5 is formed by directly welding the shell 2 of the pump impeller 1 to the front cover 4 and integrating them with each other. Damper mass 12 and front cover 4 arranged facing each other
A thrust bearing 40 is disposed between the two. Therefore, the space between the front cover 4 and the damper mass 12 communicates with the space between the damper mass 12 and the lock-up piston 14, and the hydraulic chamber 28 shown in FIG. 1 is not formed.

To prevent leakage of hydraulic pressure for engaging the lock-up clutch 11, a directional lip seal 41 is provided.
Are provided on the outer peripheral portion of the lock-up piston 14. The structure of the lip seal 41 is shown in a sectional view in FIG. That is, a lip 42 made of an elastic material such as rubber is held at the left end in FIG. 5 by an annular holder 43, and the right end of the lip 42 is pressed against the lock-up piston 14 by a spring against the outer peripheral surface. I have. Therefore, when the pressure on the right side in FIG. 5 is high, the lip portion 42 is in close contact with the outer peripheral surface of the lock-up clutch 14 to ensure liquid tightness, and conversely, when the pressure on the left side in FIG. The lip portion 42 separates from the outer peripheral surface of the lock-up clutch 14 against the elastic force of the spring,
The left and right sides are connected.

Therefore, if hydraulic pressure is supplied in the direction of arrow A in FIG. 4, the gap between the outer peripheral portion of the lock-up piston 14 and the inner peripheral surface of the housing 5 is sealed by the lip seal 41, and the lock-up piston 14 is FIG.
And the lining material 15 comes into contact with the damper mass 12 so as to be able to transmit torque. That is, the lock-up clutch 11 enters the engaged state. When the oil pressure is supplied in the direction of arrow B and the pressure is released in the direction opposite to arrow A in FIG.
When the oil flows from the left side to the right side across the lock-up piston 14, the lock-up piston 14 retreats rightward in FIG. 4, and as a result, the lining material 15 is moved to the damper mass 12. Move away from
That is, the lock-up clutch 11 enters the released state.
Since the thrust bearing 40 receives a force for pushing the damper mass 12 toward the inner surface of the front cover 4, the damper mass 12 is separated from the inner surface of the front cover 4,
And it is held rotatably.

In the configuration shown in FIG. 4, the configuration other than the configuration described above is the same as that of the torque converter shown in FIG. 1, and therefore, in the torque converter shown in FIG. It is possible to improve attenuation characteristics such as a muffled sound.

The example shown in FIG. 6 is different from the lip seal 41 shown in FIGS.
And a check ball valve 45. That is, a seal member 44 such as a seal ring is fitted around the outer periphery of the lock-up piston 14 to ensure liquid tightness with the housing 5. In the part of
A check ball valve 45 that closes when the pressure on the back side of the lock-up piston 14 is high is provided. The other configuration is the same as the configuration shown in FIG.

Therefore, when the hydraulic pressure is supplied from the direction of arrow A in FIG. 6, the check ball valve 45 is closed and the pressure on the back side of the lock-up piston 14 increases, so that the lock-up piston 14 moves to the damper mass 12 side. As a result, the lining material 15 comes into contact with the damper mass 12 so as to transmit torque. In this case, the lock-up piston 14 pushes the damper mass 12 toward the front cover 4, but the damper mass 12 is rotatably held by a thrust bearing 40 disposed between the damper mass 12 and the front cover 4. Does not come into frictional contact with the front cover 4.

The example shown in FIG.
The seal between the housing 5 and the lock-up piston 14 is formed or the seal is released depending on the position of the lock-up piston 14 in the axial direction by forming the tapered surface 46 on the outer peripheral surface of the lock 4. It is. That is, the outer peripheral surface of the lock-up piston 14
As shown in FIG. 8, a tapered surface 46 having a gradually decreasing diameter is formed on the left side of the drawing, and a seal ring 47 is fitted on the inner surface of the housing 5 so as to be located on the outer peripheral side of the tapered surface 46. ing. These tapered surfaces 46
And the seal ring 47 is a lip seal 4 shown in FIG.
1 and the other configuration is the same as the configuration shown in FIG.

In the configuration shown in FIG. 7, when the hydraulic pressure is supplied from the direction of arrow A, the lock-up piston 14
Of the hydraulic pressure supplied in the direction of arrow A can be prevented, and the lock-up piston 14 moves to the damper mass 12 side. The lock-up clutch 11 is engaged. The damper mass 12 is held by the thrust bearing 40 at a position separated from the inner surface of the front cover 4.

In the example shown in FIG. 9, in place of the extension member 3 shown in FIG. 1, a ring-shaped intermediate member 50 having a positioning projection 49 protruding in the axial direction is provided with the shell 2 of the pump impeller 1 and the front cover 4. And the positioning projection 49 is brought into contact with the center plate 30,
This is an example in which positioning of the damper mechanism 13 in the axial direction is performed. In the example shown in FIG.
Is not provided. The other configuration is the same as the configuration shown in FIG.

Therefore, in the torque converter shown in FIG. 9, as in the torque converter shown in FIG. 1, the damping characteristics of the vibration caused by the fluctuation of the input torque and the effect of preventing the muffled sound are excellent. The hydraulic pressure allows the damper mass 12 to be kept away from the front cover 4 and the lock-up piston 14 serves as a power transmission element, thereby reducing the number of parts and reducing the size and weight. Can be. In addition, since the damper mass 12 is supported by the front cover 4, the center axes of the two coincide exactly with each other, and there is no possibility of generating vibration or noise during high-speed rotation.

In the example shown in FIG. 10, the positioning member 49 is formed on the shell 2 of the pump impeller 1 so that the intermediate member 50 described above is eliminated, and the front cover 4 is provided at a portion near the center of the hub 7. Boss part 5 protruding to the side
1 is formed, and a damper mass 12 is rotatably fitted to the damper mass 12 via a bush 52 here. In FIG. 10, the other configuration is the same as the configuration shown in FIG. Therefore, also in the torque converter shown in FIG. 10, the vibration damping characteristics can be improved, the occurrence of muffled noise can be prevented, and the size and weight can be further reduced.

In the example shown in FIG. 11, the engagement force of the lock-up clutch 11 is increased by sandwiching the lock-up piston 14 between two types of damper masses. In the following description, the same components as those shown in FIG. 1 are denoted by the same reference numerals in FIG. 11 as those in FIG. 1, and the description thereof will be omitted.

In FIG. 11, the shell 2 of the pump impeller 1 is integrated by welding to the front cover 4, and the shell 2 and the front cover 4 form a torque converter housing 5. Further, three damper masses 53, 54, 55 are provided as rotating inertial mass bodies. The first damper mass 53 is disposed along the inner surface of the front cover 4 and has a turbine runner 6
A cylindrical portion 56 protruding to the side is formed. On the other hand, annular projections 57 and 58 are formed on the inner surface of the front cover 4 at the outer peripheral portion and the central portion, and the intermediate portion has a long protruding length and is not continuous in the circumferential direction. Two rows of projections 59 and 60 are formed, and the first damper mass 53 is fitted on the outer periphery of the annular projection 58 on the center side via a needle bearing 61 and is rotatably supported here. The first damper mass 53 is also fitted to the annular projection 57 on the outer peripheral side, and the annular projection 57 is sealed by a seal ring 62. First
A needle bearing 63 as a reaction force means is interposed between a portion of the damper mass 53 on the outer peripheral side of the annular protrusion 57 and the front cover 4, whereby the position of the first damper mass 53 in the axial direction is adjusted. The first damper mass 53 is determined and is rotatably supported by the front cover 4.

The projections 59 and 60 arranged at two different radial positions serve as stoppers for the damper spring 29. The coil spring 29 is provided between the projections 59 and 60 in each row. Are located. The first damper 53 is provided with an opening for fitting these coil springs 29. Therefore, when the front cover 4 and the first damper mass 53 rotate relative to each other, the coil springs The protrusions 59 and 60 press one end of the coil 29 and the other end is pressed by one end of the opening of the first damper mass 53 to compress the coil spring 29.

The second damper mass 54 is disposed in close contact with the surface of the first damper mass 53 opposite to the surface on the front cover 4 side, and is connected so as to be integrated with the rivets 23. An opening for accommodating the coil spring 29 is also formed in the second damper mass 54.

Further, the third damper mass 55 is a block member that moves in the axial direction, whereas the second damper mass 54 is a block member that is fixed in the axial direction. The damper mass 55 is formed as an annular member having a trapezoidal cross section or a triangular cross section as shown in the figure. Also, the third damper mass 55 is
Of the cylindrical portion 56 of the damper mass 53 is spline-fitted, prevented by a snap ring 64, and further sealed by a seal ring 65.

An outer peripheral portion of the lock-up piston 14 is inserted between the second damper mass 54 and the third damper mass 55. The lock-up piston 14 is fitted to the outer peripheral portion of the hub 7 in the axial direction by a spline 66 so as to be able to move in the axial direction and transmit a torque, and is an annular plate sealed with a seal ring 67 provided on the inner peripheral side thereof. And the outer peripheral part of the outer peripheral part (second surface)
The lining material 15 is attached to each of the surfaces facing the damper mass 54 and the third damper mass 55). Therefore, the lock-up clutch 11 is configured such that both front and back surfaces of the lock-up piston 14 are friction surfaces (torque transmitting surfaces).

Note that the outer peripheral end of the lock-up piston 14 is separated from the inner peripheral surface of the cylindrical portion 56 of the first damper mass 53, and the second lining material 15 which is on the low pressure side when engaged. In the lining material 15 on the damper mass 54 side, a number of radial grooves (not shown) are formed from the inner peripheral end to the outer peripheral end. Therefore, even if the lining material 15 is in close contact with the second damper mass 54, the gap between the other lining material 15 and the third damper mass 55 is formed by the concave groove so that the lock-up piston 14 and the second The space between the damper mass 54 and the damper mass 54 is communicated.

In the torque converter shown in FIG.
When hydraulic pressure is supplied in the direction of arrow A, the lock-up piston 14 is pressed toward the second damper mass 54, and the lining material 15 comes into contact with the second damper mass 54 so as to be able to transmit torque. Since the groove is formed in the lining material 15 as described above, the pressure between the third damper mass 55 and the lock-up piston 14 is reduced, and as a result, the third damper mass 55 is locked. Move the up piston 14 so as to push it toward the second damper mass 54,
It comes into contact with the lining material 15 so as to transmit torque. That is, the second and third damper masses 54 and 55 sandwich the outer peripheral portion of the lock-up piston 14, and the lock-up clutch 11 is engaged. Then, the input torque is transmitted from the front cover 4 to the damper masses 53, 54, 55 via the damper spring 29, and further transmitted to the hub 7 as an output member via the lock-up piston 14.

Therefore, also in the torque converter shown in FIG. 11, the damper masses 53, 54, 55 are connected to the front cover 4 via the damper spring 29, and the damper masses 53, 54, 55 are connected to the front cover 4 by the needle bearing 63. 4 is held so as not to make frictional contact, so that vibration damping characteristics are excellent, and muffled noise can be effectively prevented. Further, since the lock-up piston 14 also serves as a torque transmitting element, the number of parts can be reduced and the size and weight can be reduced. Further, since the damper masses 53, 54, 55 are supported by the front cover 4, the center axes of the two can be accurately matched, and vibration and noise during high rotation can be effectively prevented. Since the space between the damper masses 53, 54, 55 and the front cover 4 is sealed by a seal ring 62 provided between the annular projection 57 on the outer peripheral side and the first damper mass 53, the lock-up clutch 11 Can be prevented from leaking.

The example shown in FIG. 12 is an example in which the third damper mass 55 is eliminated from the configuration shown in FIG. In the torque converter shown in FIG. 12, the engagement area of lock-up clutch 11 is reduced by half as compared with the torque converter shown in FIG. 11, but the same operation and effect as in the torque converter shown in FIG. 11 can be obtained.

The example shown in FIG. 13 is an example in which the engagement area of the lock-up clutch 11 is increased, and a bush and a hydraulic chamber are used as reaction force means. That is, the first damper mass 68 arranged along the inner surface of the front cover 4 has a cylindrical portion 69 extending in the axial direction at the outer peripheral end.
The first damper mass 68 is provided with an annular protrusion 58 protruding from a position near the center of the front cover 4.
The fitted rotatably through a bush 70, the radial position Contact and axial direction is determined by the bush 70. Another annular projection 57 is formed on the inner surface of the front cover 4 near the outer periphery, and the first damper mass 68 is fitted to the annular projection 57 and is sealed by the seal ring 62. Further, an annular second damper mass 71 having a substantially triangular cross section or a substantially trapezoidal cross section is spline-fitted on 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. I have.

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. The lining material 15 on the first damper mass 68 side has a concave groove (not shown) extending from the inner peripheral end to the outer peripheral end.

The lock-up piston 1 of the example shown in FIG.
4 is connected to the hub 7 via the intermediate member 72.
The intermediate member 72 is fixed to the hub 7 together with the turbine runner 6 at an inner peripheral portion thereof, and a cylindrical portion 73 having an outer diameter substantially equal to the inner diameter of the annular projection 57 near the outer periphery of the front cover 4 is formed on the outer peripheral portion. Have been. The lock-up piston 14 is fitted to the cylindrical portion 73 movably in the axial direction, and is sealed by a seal 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 lock-up piston 14.
Further, the lock-up piston 14 and the intermediate member 72 are connected so as to be able to transmit torque by convex and concave portions 75 formed respectively so as to mesh with each other in the circumferential direction.
The other configuration is almost the same as that of the torque converter shown in FIG. 11, and therefore, the same reference numerals as in FIG. 11 are assigned to FIG. 13 and the description is omitted.

Therefore, also in the torque converter shown in FIG. 13, the damper mass 68 can be maintained at a distance from the front cover 4 when the lock-up clutch 11 is engaged, and the mass of the damper mechanism 13 can be increased. Excellent characteristics and muffled sound prevention effect.

FIG. 14 shows a modification of the torque converter shown in FIG. 12, in which a hydraulic chamber 28 is employed as a reaction force means instead of the needle bearing 63. That is, the damper mass 12 is rotatably fitted via the bush 52 to an annular projection 58 protruding from a position near the center of the front cover 4, and is sealed by the seal ring 27. Since the seal portion is formed at a position closer to the center in this way, the third portion which is not continuous in the circumferential direction is formed at a position closer to the outer periphery of the inner surface of the front cover 4.
Are formed on both ends of the damper spring 29 held by the damper mass 12.
, The damper spring 29 is compressed with the damper mass 12. The lock-up piston 14 is directly fixed to the hub 7.

With the configuration shown in FIG. 14, the hydraulic chamber 28 is provided between the inner surface of the front cover 4 and the damper mass 12.
Is formed, and the hydraulic pressure for engaging the lock-up clutch 11 also acts on the hydraulic chamber 28 to keep the damper mass 12 separated from the front cover 4. Therefore, the sliding resistance when the damper mass 12 rotates relative to the front cover 4 decreases. That is, the damper characteristic has a small hysteresis, and the tendency is shown in FIG.
It is shown in In FIG. 15, the broken line indicates the damper characteristic of the torque converter shown in FIG. 14, and the dashed line indicates the damper characteristic of the torque converter using the thrust bearing as the reaction force means. Therefore, if a means having a small frictional resistance such as a hydraulic chamber is used as the reaction force means, the damper characteristics are improved, which is advantageous for preventing a muffled sound.

The present invention can be applied to a fluid coupling having no torque amplifying function, in addition to the above-described torque converter.

[0069]

As described above, in the present invention, the rotating inertial mass is connected to the housing via the elastic body of the damper mechanism, and the lock-up piston operated by hydraulic pressure is connected to the rotating inertial mass. And a reaction force means for holding the rotary inertia mass body in a non-contact state with the inner surface of the front cover when the lock-up clutch is engaged, so that the rotary inertia mass body is provided. Performs the same operation as the flywheel damper, and can effectively attenuate the vibration caused by the fluctuation of the input torque. In addition, when the lock-up clutch is engaged, the rotating inertial mass does not contact the front cover, and there is no sliding friction between the two, so that the damper characteristics have little hysteresis, and it is possible to effectively prevent booming noise. it can. Furthermore, when the lock-up clutch is released, the lock-up piston acts as an inertial resistance to the output member, but the mass required for the damper mechanism is secured by the rotating inertial mass, and the lock-up piston is lightweight. Therefore, the amount of synchronization energy applied to the clutch of the automatic transmission during shifting is reduced, which is advantageous in reducing shift shock. It should be noted also, the lock-up clutch, since the control of engagement and disengagement by hydraulic pressure, control sex
It is improved.

When the rotary inertial mass body is supported by the front cover, the center axes of the two are exactly coincident with each other, and the generation of vibration and noise during high-speed rotation can be prevented.

Further, if the lock-up piston is connected to the output member so that torque can be transmitted, the lock-up piston functions as a transmission element from the damper mechanism to the output member, so that the number of parts is reduced and the size and weight are reduced. Can be.

When the radius of the seal portion on the inner peripheral side of the rotary inertia mass body and the radius of the seal portion on the inner peripheral side of the lock-up piston brought into contact with the rotary inertia mass body are made substantially equal, the lock-up piston becomes Since the pushing force and the opposing force are balanced, the rotating inertial mass can be kept away from the front cover without increasing the sliding resistance, thereby improving the vibration damping characteristics. Can be.

[Brief description of the drawings]

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

FIG. 2 is a view showing a lock-up piston,
(A) is a partially omitted front view, and (B) is BB of (A).
It is a line sectional view.

FIG. 3 is a view showing a hub, wherein (A) is a front view,
(B) is a sectional view taken along line BB of (A).

FIG. 4 is a partial sectional view showing a second embodiment of the present invention.

FIG. 5 is an enlarged sectional view of a lip seal according to a second embodiment.

FIG. 6 is a partial sectional view showing a third embodiment of the present invention.

FIG. 7 is a partial sectional view showing a fourth embodiment of the present invention.

FIG. 8 is a sectional view showing a seal structure of an outer peripheral portion of a lock-up piston according to a fourth embodiment.

FIG. 9 is a partial sectional view showing a fifth embodiment of the present invention.

FIG. 10 is a partial sectional view showing a sixth embodiment of the present invention.

FIG. 11 is a partial sectional view showing a seventh embodiment of the present invention.

FIG. 12 is a partial sectional view showing an eighth embodiment of the present invention.

FIG. 13 is a partial sectional view showing a ninth embodiment of the present invention.

FIG. 14 is a partial sectional view showing a tenth embodiment of the present invention.

FIG. 15 is a damper characteristic diagram.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Pump impeller 2 Shell 4 Front cover 5 Housing 6 Pump impeller 7 Hub 11 Lockup clutch 12 Damper mass 13 Damper mechanism 14 Lockup piston 17 Projection 19 Seal ring 20 Projection 24 Annular projection 27 Seal ring 28 Hydraulic chamber 29 Damper spring Reference Signs List 40 thrust bearing 41 lip seal 44 seal member 45 check ball valve 46 taper surface 47 seal ring 53, 54, 55 damper mass 58 projection 61 needle bearing 62 seal ring 63 needle bearing 65 seal ring 66 spline 67 seal ring 68 damper mass 70 bush 71 Tamper mass 74 Seal ring 75 Irregularities

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-63-251664 (JP, A) JP-A-4-151056 (JP, U) (58) Fields investigated (Int. Cl. ⁶ , DB name) F16H 45/02 F16D 33/18

Claims (4)

(57) [Claims] 1. A housing is formed by an outer shell of a pump impeller for generating a fluid flow and a front cover integrally connected to the outer shell, and a turbine runner is disposed in the housing so as to face the pump impeller. Wherein a lock-up clutch for selectively transmitting torque between the housing and an output member integrated with the turbine runner is provided in the housing. A rotating inertial mass that is relatively rotatable is disposed between the inner surface of the front cover and the turbine runner and on the same axis as the housing, and when the rotating inertial mass is relatively rotated with respect to the housing. A damper mechanism having an elastic body compressed to A lock-up piston, which is moved back and forth by a fluid pressure in the axial direction of the housing and is in contact with the rotating inertial mass so as to be able to transmit torque and is separated from the bin runner so as not to transmit torque, is further provided between the bin runner and the lock-up piston. When the up piston contacts the rotating inertial mass body, a reactive force means for applying a reaction force to the rotating inertial mass body toward the lock-up piston side to maintain the rotating inertial mass body in a non-contact state with respect to the inner surface of the front cover. Provided, and when the lock-up piston contacts the rotating inertial mass,
The space between the rotating inertial mass body and the turbine run
A fluid transmission device with a lock-up clutch, wherein a seal means for sealing the space portion on the side of the nut in a non-communication state is provided. 2. An annular projection protruding in the axial direction is formed on an inner surface of the front cover, and the rotary inertia mass body is rotatably fitted to the annular projection and is positioned on the same axis as the housing. 2. The method according to claim 1, wherein
The fluid transmission device with a lock-up clutch according to the above. 3. The lock-up clutch according to claim 1, wherein the lock-up piston is non-rotatably connected to the output member so as to transmit torque to an output member integrated with the turbine runner. With fluid transmission. 4. An annular projection is formed on an inner surface of the front cover.
Formed on the annular projection on the inner peripheral portion of the rotating inertial mass body
There is rotatably fitted, and these annular projection and rotational inertia protein
A seal portion that seals a fitting portion with the volume body in a liquid-tight state is provided, and the lock-up piston is fitted to an output member integral with the turbine runner while maintaining the liquid-tight state, and the fitting is performed. The fluid transmission device with a lock-up clutch according to claim 1, wherein a radius from a rotation center of the portion and a radius of the seal portion are set substantially equal.