JP2836396B2 - 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 fluid transmission device having a lock-up clutch such as a torque converter in an automatic transmission for a vehicle, and more particularly to a structure for holding a damper mechanism.

[0002]

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

[0003] The structure thereof will be briefly described. Referring to FIG. 6, a turbine runner 5 is disposed inside a housing 3 including a pump shell 1 and a front cover 2 so as to face a pump impeller 4. The stator 7 supported by the one-way clutch 6 is disposed between the two.
The lock-up clutch 8 is fitted to an outer peripheral portion of a hub 10 to which the turbine runner 5 is fixed by rivets 9 while being sealed by a seal ring 11 so as to be movable in an axial direction. A plurality of engagement teeth 12 are formed on the inner peripheral portion of the lock-up clutch 8, and the engagement teeth 12 are rotationally engaged with projections (not shown) formed on the hub 10, so that the lock-up clutch 8 is rotated. It rotates integrally with the hub 10 and the turbine runner 5.

[0004] A damper mechanism 13 is provided between the lock-up clutch 8 and the front cover 2. The damper mechanism 13 includes a center plate 15 holding a plurality of damper springs 14 oriented in a circumferential direction or a tangential direction, and a rivet 16 sandwiching the damper springs 14 and the center plate 15 therebetween.
Main member 17 and cover member 18 integrated by
And a damper mass 19 composed of
The center plate 15 is integrated with the housing 3 in the rotation direction by engaging the protrusion 20 formed on the outer periphery with the inner periphery of the housing 3, and thus the center plate 15 serves as a driving member. ing.

The lock-up clutch 8 is configured to selectively engage with a damper mass 19 via a lining material 21 attached to a side surface of an outer peripheral portion of the lock-up clutch 8. Therefore, the damper mass 19 serves as a driven member. I have. The damper mechanism 13 is configured to bend the projection 20 formed on the outer peripheral portion of the center plate 15 in the axial direction, and abut the extended portion 22 formed on the outer peripheral portion of the pump shell 1 against the projected portion 20. Projection 2 of plate 15
0 is sandwiched between the extension portion 22 and the inner surface of the front cover 2 to perform positioning in the axial direction.

[0006]

In the damper mechanism 13 having the above-described damper mass 19, the damper mass 19
Is required to be rotatable with respect to the input side member such as the front cover 2, so that the positioning in the axial direction is performed by the outer peripheral side projection 20 of the center plate 15, which is the driving member, and the pump shell 1. The extension 22 is performed. Therefore, in the above-described conventional device, the outer diameter of the damper mechanism 13 is
The outer diameter of the housing 3 increases with the formation of 0.

[0007] As described above, in the above-mentioned conventional apparatus, there is a factor that the outer diameter is increased, and there is a possibility that the in-vehicle property is deteriorated and the weight is increased, and there is room for improvement in these points.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a hydraulic power transmission with a lock-up clutch which can be reduced in size and weight.

[0009]

According to the present invention, in order to achieve the above object, at least two members are joined to form a housing, and a pump impeller and a turbine runner are arranged in the housing. 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, and a drive member and a lock-up clutch connected to the housing so as to rotate integrally therewith are provided. In a fluid transmission with a lock-up clutch provided with a damper mechanism in which a driven member to be selectively engaged is connected via an elastic body exhibiting elasticity in a circumferential direction, a joint portion between the two members is the damper mechanism. Abutting portions are formed on the outer peripheral side of the shaft and are opposed to each other in the axial direction at the joints thereof. Member is interposed a portion of the periphery to the butted portion is positioned in the axial direction,
The drive member and the lock-up of the driven member.
The frictional engagement part with which the clutch engages
At a different position .

[0010]

The housing in the present invention is formed by joining at least two members such as a pump shell and a front cover. An abutting portion that is opposed in the axial direction is formed at the joint portion,
The outer peripheral portion of the drive member of the damper mechanism is interposed between the butted portions, and thus the drive member is positioned and held by the housing, whereby the damper mechanism is positioned in the axial direction. That is, the joint portion also serves as a positioning means of the damper mechanism, and therefore, the diameter of the housing is reduced . Also, damper
-At least two members are butted against the outer periphery of the mechanism
Part is arranged, and a driving member is
And the drive member and the friction engagement portion are at different positions in the axial direction.
And the driving member and the driven member are arranged in a damper machine.
It is connected via a structure. Therefore, the torque to transmit
The area of the frictional engagement part and the radial dimension
When setting specifications, there is no restriction on the dimensions of the driving member
Can be set to the above specifications.

[0011]

Next, an embodiment of the present invention will be described with reference to the drawings. Since the embodiment described below is an improvement of the conventional torque converter shown in FIG. 6, the same parts and members as those shown in FIG. 6 have the same reference numerals as those shown in FIG. The reference numerals are attached to the drawings and the description is omitted.

FIG. 1 shows an embodiment of the present invention.
The outer peripheral tip of the pump shell 1 in the torque converter shown here extends to the outer peripheral side of the damper mechanism 13. The outer peripheral portion of the front cover 2 is bent at approximately 90 ° toward the pump shell 1 side, and the bent cylindrical portion is fitted to the inner peripheral side of the distal end portion of the pump shell 1. In this state, the pump shell 1 and the front cover 2 are joined by welding 23.

FIG. 2 shows a part of this joint.
The inner peripheral portion of the distal end portion of the pump shell 1 is cut off over the entire circumference at a thickness of approximately half the plate thickness, and a fitting portion 24 having a predetermined length in the axial direction is formed in this portion. . The outer diameter of the front cover 2 is set to be substantially the same as the inner diameter of the fitting portion 24, and the outer peripheral cylindrical portion of the front cover 2 is closely fitted into the fitting portion 24 and fitted. At the tip of the cylindrical portion formed by bending the front cover 2 in the axial direction, a notch 25 cut into a rectangle at a depth corresponding to the thickness of the center plate 15 which is a driving member of the damper mechanism 13 is provided. Are formed at regular intervals in the circumferential direction. Further, on the outer peripheral portion of the center plate 15, projections 26 to be inserted into the notches 25 are formed at equal intervals to the notches 25. The front cover 2 is fitted inside the fitting portion 24 of the pump shell 1 with the projection 26 of the center plate 15 inserted into the notch 25.

Therefore, the face 24a of the fitting portion 24 facing the axial direction and the face 25 of the notch portion 25 facing the axial direction.
a is a butting portion facing each other, and the center plate 15 is positioned in the axial direction by interposing the protruding portion 26 at the butting portion, and is integrated with the housing 3.

The damper mechanism 13 whose axial position is determined as described above is centered by the front cover 2. That is, the main member 17 constituting the damper mass 19 is an annular member, and the cylindrical portion on the inner peripheral side thereof is rotated on the outer peripheral surface of the annular protrusion 27 provided on the inner surface of the front cover 2. By being fitted as much as possible, it is held on the same axis as the housing 3.

A boss 28 having an outer diameter substantially equal to the outer diameter of the hub 10 is formed on the inner surface of the front cover 2, and an annular projection 29 formed on the main member 17 is formed on the boss 28. Fitted in non-contact state. This boss 2
The space between the annular projection 8 and the annular projection 29 is sealed in a liquid-tight state by a seal ring 30 attached to the boss 28. Therefore, between the inner surface of the front cover 2 and the damper mechanism 13, when the lock-up clutch 8 is engaged, a portion to which the hydraulic pressure for engaging the lock-up clutch 8 is supplied, that is, a position closer to the turbine runner 5 than the lock-up clutch 8. A hydraulic chamber 31 communicating with the portion is formed.

[0017] Reference numeral 32 denotes a lock-up piston 1, the lock-up piston 32 is mainly
It is arranged between the member 17 and the turbine runner 5.
The lock-up piston 32, by fitting the cylindrical portion 33 which is formed on the inner peripheral portion of it to the outer peripheral boss 34 of the hub 10 is supported by the hub 10.
A projection 35 formed on the outer peripheral side surface of the hub 10
Are engaged with the engagement teeth 12 of the lock-up piston 32 . Further, in the lock-up piston 32,
A lining is provided on the outer peripheral side of the side surface facing the main member 17
Material 21 is attached. This lockup fixie
1 moves to the left in FIG.
The side surface of the member 17, that is, the frictional engagement portion comes into contact.
In this embodiment, the center plate 15 is
Between the member 17 and the cover member 18 from both sides in the axial direction.
It is configured to be found. That is, the main member 17
And the side opposite the center plate 15
The contact material 21 comes into contact. Therefore, center play
15 and the friction engagement portion are arranged at different positions in the axial direction.
Have been.

In FIG. 1, reference numeral 36 denotes a friction plate.
It is a generally annular member formed with elastically deformed arcuate cross sections 37 at regular intervals. The friction plate 36 is arranged on the inner surface side of the front cover 2 so that the arcuate cross-section 37 is located at a punched portion formed at a predetermined interval in the circumferential direction on the cover member 18. The arcuate section 37 is elastically deformed and sandwiched between the front cover 2 and the center plate 15, and the elastic force causes the arcuate section 37 to strongly adhere to the inner surface of the front cover 2 and the center plate 15. It is imposed. Although not particularly shown, a friction material is attached to a portion of the friction plate 36 facing the inner surface of the front cover 2.

The torque converter described above transmits torque by supplying a fluid flow generated by the pump impeller 4, that is, a spiral flow of oil to the turbine runner 5 and rotating the turbine runner 5. The interior is filled with oil. The lock-up clutch 8 is a clutch that engages and disengages in accordance with a pressure difference between both sides of the lock-up piston 32, so that the lock-up clutch 8 is provided in the space on the turbine runner 5 side with respect to the lock-up piston 32. 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 32 and damper mass 19 (oil passage indicated by arrow B in FIG. 1) are provided. Is formed.

As is known from the configuration shown in FIG.
When the lock-up piston 32 moves to the left in FIG. 1 and the lining material 21 comes into contact with the damper mass 19 so that torque can be transmitted, that is, when the lock-up clutch 8 is engaged, the hydraulic chamber 31 locks with the damper mass 19. Although there is no communication between the lockup piston 32 and the lockup piston 32, the lockup piston 32 communicates with the turbine runner 5, 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 8 also acts on the hydraulic chamber 31.

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 8 is released. In this case, hydraulic pressure is supplied from the direction of arrow B to increase the hydraulic pressure between the lock-up piston 32 and the damper mass 19. Thereby, the lockup piston 32 is separated from the damper mass 19. When torque is applied to the front cover 2 from an engine (not shown) in this state, the pump impeller 4 rotates together with the housing 3 to generate a spiral flow of oil. By providing the spiral flow to the turbine runner 5, torque is transmitted to the turbine runner 5 and the turbine runner 5 rotates together with the hub 10. The torque is transmitted to the automatic transmission via an input shaft (not shown) fitted to the hub 10.

On the other hand, since the damper mass 19 is connected to the housing 3 by the damper mechanism 13 including the center plate 15 and the damper spring 14, it rotates integrally with the housing 3. In this case, the damper mass 19 has its main member 17 fitted into the annular projection 27 of the front cover 2 and the damper mass 19 is positioned on the same axis as the front cover 2. Does not vibrate or generate abnormal noise. In addition, since the inertia mass of the damper mass 19 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 damped or controlled.

When the lock-up clutch 8 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 21 and the main member 1
7, the pressure in the space between the lock-up piston 32 and the main member 17 decreases due to the orifice effect of this portion, and the lock-up piston 3
2, the pressure in the space on the turbine runner 5 side from the lock-up piston 32 becomes higher. As a result, the lock-up piston 32 relatively approaches the damper mass 19 and the lining material 21 comes into contact with the side surface of the main member 17 so as to be able to transmit torque.

In this case, the hydraulic chamber 31 is
By the damper mass 19 and the lock-up piston 3
2 and is connected to the high pressure portion on the turbine runner 5 side, the pressure in the hydraulic chamber 31 causes the lockup piston 32 to move the lockup piston 32 to the damper mass 19. Side pressure. Since the radius of the seal portion on the inner peripheral side defining the hydraulic chamber 31 is equal to the radius of the seal portion on the inner peripheral side of the lock-up piston 32, the load pushing the lock-up piston 32 leftward in FIG. 1 is balanced with the load that pushes the damper mass 19 rightward in FIG. 1, so that the damper mass 19 is kept at a position away from the inner surface of the front cover 2.

Therefore, the input torque transmitted to the front cover 2 is transmitted to the damper mass 19 via the damper spring 14 of the damper mechanism 13, and further transmitted from the damper mass 19 to the lock-up piston 32.
Is transmitted to When the input torque fluctuates, the damper mass 19 is rotatable with respect to the housing 3 and the lock-up piston 32 is in contact with the damper mass 19 so as to transmit torque.
Members such as 9 and the lock-up piston 32 act as inertial resistance. As a result, the damper spring 14 is compressed according to the change in the input torque, and the damper spring 1
4 absorbs vibration.

In the lock-up piston 32, the engagement teeth 12 formed on the inner periphery of the lock-up piston 32
0, the torque transmitted from the damper mass 19 to the lock-up piston 32 is transmitted through the engagement teeth 12 and the projection 35 to the hub 10. Is transmitted to

In the structure shown in FIG. 1, when the energy stored in the damper spring 14 is released, the friction plate 36 slides more between the damper mass 19 of the damper mechanism 13 and the inner surface of the front cover 2. Because of the resistance, a part of the emitted energy is absorbed by the sliding part. In other words, when the relative rotation between the damper mass 19 and the driving-side member such as the center plate 15 increases due to the large fluctuation of the input torque, the arcuate section 37 of the friction plate 36
There is no gap in the circumferential direction between the punching portion of the cover member 18 and the friction plate 36 and the damper mass 19.
Rotate integrally, and the friction plate 36 slides with respect to the front cover 2. The sliding resistance at that time acts so as to suppress the relative rotation of the damper mass 19, and as a result, a "hiccup" phenomenon, which is a long fluctuation of the wavelength of the output shaft torque, is prevented, and the riding comfort is improved. Further, when the fluctuation of the input torque is small, a gap is formed in the circumferential direction between the arcuate section 37 of the friction plate 36 and the punched portion of the cover member 18, and the friction plate 36 outputs the output of the damper mass 19 or the like. Since there is no contact with the member on the side, there is no adverse effect such as an increase in booming noise.

In the above torque converter, the projection 26 formed on the outer peripheral portion of the center plate 15 is interposed at the joint between the pump shell 1 and the front cover 2 so as to be sandwiched between the pump shell 1 and the front cover 2. Since the pump shell 1 and the front cover 2 are positioned, it is not necessary to form a portion protruding to the outer peripheral side. Therefore, by configuring the housing 3 as shown in FIG. 1, the diameter of the torque converter can be reduced, and the weight can be reduced.

Further , the outer peripheral side of the damper mechanism 13 is formed.
The center plate 15 is pivoted by the inclined surfaces 24a and 25a.
It is positioned in the line direction, and the center plate 15
And damper mass 19 are connected via damper mechanism 13.
And the center plate 15 and the lock-up
The side of the main member 17 with which the lining material 21 of the latch 8 is engaged
Surface (frictional engagement part) is located at a different position in the axial direction.
ing. For this reason, frictional engagement corresponding to the transmitted torque
When setting specifications such as the area of the part and the radial dimension
Above, without being restricted by the size of the center plate 15.
It is possible to set specifications. Na us, the structure of the joint portion and the butt portion of the pump shell 1 and front cover 2 in this invention has been not limited to the structure shown in FIG. 1, it may be configured as shown below.

FIG. 3 is a partial cross-sectional view showing another example of the joint between the pump shell 1 and the front cover 2. In the example shown here, the end of the pump shell 1 and the end of the front cover 2 are shown. Meshing portions 1a and 2a that mesh with each other in the plate thickness direction are formed in each of the portions, and the protrusion 26 of the center plate 15 is inserted into the inner peripheral side of the meshing portion 2a of the front cover 2, and The meshing portion 1a of the pump shell 1 is abutted on the side surface. Therefore, the center plate 15 is positioned in the axial direction by the joint between the pump shell 1 and the front cover 2, and is integrated with the housing 3. In the example shown in FIG. 3, the meshing portions 1a and 2a are butting portions that are opposed in the axial direction for holding the center plate 15.

In the example shown in FIG. 4, a center plate 1 is attached to the end of the pump shell 1 and the end of the front cover 2.
Forming notches 1b and 2b having a depth of half the thickness of the plate 5;
The notch 1b, 2b sandwiches the projection 26 of the center plate 15 in a state where the pump shell 1 and the front cover 2 are butted and welded. In the structure shown in FIG. 4, the notches 1b and 2b serve as abutting portions, and the center plate 15 has its protrusion 26 interposed between the notches 1b and 2a in the axial direction. Positioned.

Further, in the example shown in FIG. 5, a spline 40 is formed on the inner surface at the end of the front cover 2 and the outer peripheral portion of the center plate 15, and
Is engaged with the front cover 2 by the spline 40, and in this state, the side surface is pressed in the axial direction by the end of the pump shell 1 inserted in the front cover 2. Therefore, in the structure shown in FIG.
The center plate 15 is sandwiched and positioned between the front cover 2 and the pump shell 1 in the axial direction.

In any of the structures shown in FIGS. 3 to 5, there is no particular factor that causes the housing 3 to protrude toward the outer periphery, so that the diameter and weight of the torque converter can be reduced.

It should be noted that the present invention is not limited to the above embodiments, and the housing may be formed by using an extension member joined to any of the front cover and the pump shell in addition to the front cover and the pump shell. In this case, the driving member of the damper mechanism may be held at the joint with the extension member. Further, the present invention is not limited to the torque converter, and can be applied to a fluid coupling having no torque amplifying action.

[0035]

As described above, according to the present invention,
Because a part of the outer periphery of the drive member of the damper mechanism is interposed at the joint of the members constituting the housing, and the drive member is sandwiched between the butting portions facing each other in the axial direction to perform positioning in the axial direction. , The joint of those members will also serve as the positioning means of the damper mechanism,
As a result, according to the present invention, factors that cause the housing to protrude to the outer peripheral side are reduced, so that the overall diameter can be reduced, and the fluid transmission device can be reduced in size and weight .
Also, at least two members are provided on the outer peripheral side of the damper mechanism.
Of the drive unit
The drive member and the frictional engagement part are axially
And the driving member and the driven member
Are connected via a damper mechanism. Therefore,
The area of the friction engagement part and the radial direction corresponding to the transmitted torque
When setting specifications such as the dimensions of
The above specifications can be set without any restrictions.

[Brief description of the drawings]

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

FIG. 2 is a schematic partial exploded perspective view showing a joint portion of the housing.

FIG. 3 is a partial cross-sectional view showing another example of the joint according to the present invention.

FIG. 4 is a partial cross-sectional view showing still another example of a joint according to the present invention.

FIG. 5 is a partial cross-sectional view showing another example of the joint according to the present invention.

FIG. 6 is a cross-sectional view of a fluid transmission device with a lock-up clutch already proposed by the present applicant.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Pump shell 2 Front cover 3 Housing 4 Pump impeller 5 Turbine runner 8 Lock-up clutch 13 Damper mechanism 14 Damper spring 15 Center plate 19 Damper mass 24 Fitting part 25 Notch part 26 Projection

Continuation of the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F16H 45/02 F16H 41/24 F16H 41/28

Claims (1)

(57) [Claims] At least two members are joined to form a housing, within which a pump impeller and a turbine runner are disposed, and wherein the housing and the turbine runner are selectively coupled between an output member and an output member. A lock-up clutch for transmitting torque is provided in the housing, and furthermore, a drive member connected to the housing and integrally driven to rotate and a driven member selectively engaged by the lock-up clutch exhibit elasticity in a circumferential direction. In a fluid transmission with a lock-up clutch provided with a damper mechanism connected via an elastic body, a joint between the two members is disposed on an outer peripheral side of the damper mechanism, and the joint is opposed to the joint in the axial direction. A butt portion is formed, and the driving member is provided with a part of its outer periphery interposed in the butt portion. Is positioned in the line direction, and the drive member, said driven member
A friction engagement portion with which the lock-up clutch is engaged.
Are arranged at different positions in the axial direction, wherein the fluid transmission device has a lock-up clutch.