JP3751666B2 - Flywheel device with damper mechanism - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a flywheel device with a damper mechanism.
[0002]
[Prior art]
Conventionally, for example, Japanese Patent Laid-Open No. 5-209667 discloses a flywheel device with a damper mechanism in which an inertial mass body in the damper mechanism is caused to function as a flywheel. FIG. 12 shows a longitudinal sectional view thereof. This device includes a pump 4 integrated with the front cover 2, a turbine 6 disposed opposite the pump 4, a stator 8 disposed between the turbine 6 and the pump 4, an inner surface of the front cover 2, and the turbine 6 is provided with a lock-up clutch 10 and a damper mechanism 12 disposed between the two. The inner peripheral side of the lockup clutch 10 is connected to the hub 14, and torque is transmitted to an output shaft (not shown) via the hub 14.
[0003]
The damper mechanism 12 mainly includes a driving member 16 and a driven member 20 that holds the damper spring (elastic member) 18 while sandwiching the driving member 16. The driven member 20 includes a main member (inertial mass body) 22 having a relatively large inertial mass and a cover member 24 attached to one side surface thereof. The main member 22 and the cover member 24 are connected by a rivet 23, and both are integrated in both the axial direction and the rotational direction. Further, the driving member 16 is engaged with the front cover 2 at the periphery, and rotates integrally with the front cover 2.
[0004]
When the lock-up clutch 10 is off, oil is supplied from the portion A in the figure as indicated by an arrow, the hydraulic pressure between the lock-up clutch 10 and the main member 22 is increased, and the lock-up clutch 10 is a damper mechanism. 12 main members 22 are separated. At this time, since the main member 22 receives the leftward pressure in the drawing, the main member 22 is pressed against the drive member 16 side, and the main member 22 and the drive member 16 are brought together by the friction engagement means 26 provided in this portion of the main member 22. Integrated in the direction of rotation.
[0005]
Therefore, the main member 22 acting as an inertial mass body is connected to the engine (not shown) via the front cover 2 without the damper spring 18, so that the function as a flywheel is improved.
[0006]
When the lock-up clutch 10 is on, oil is supplied in the direction of the arrow from the portion B in the figure, and the lock-up clutch 10 is moved to the main member 22 side of the damper mechanism 12. At this time, in the drawing, the pressure on the C side of the main member 22 is higher than that on the D side, the main member 22 moves to the lock-up clutch 10 side, and the friction material 28 attached to the lock-up clutch 10 faces this. It is pressed against the side surface of the main member 22 and engaged and integrated.
[0007]
Accordingly, torque is transmitted from the driving member 16 rotating integrally with the front cover 2 to the lockup clutch 10 via the damper spring 18 and the driven member 20 holding the damper spring 18.
[0008]
[Problems to be solved by the invention]
However, as described above, conventionally, the frictional engagement means is provided only at one place as shown in FIG. 12, for example, and therefore the torque transmission capacity of the frictional engagement means is inadequate. There is a problem that the inertial mass body cannot be effectively used as a flywheel.
[0009]
To simply increase the torque transmission capacity, (1) increase the effective friction area at the friction engagement means, (2) increase the effective radius of the friction surface, (3) increase the oil pressure, etc. Can be considered.
[0010]
However, the methods {circle around (1)} and {circle around (2)} cause a new problem that the size of the apparatus increases, and the method {circle around (3)} causes new problems such as an increase in pump capacity and an increase in sealing performance.
[0011]
The present invention has been made to solve the above-described conventional problems, and can increase the torque transmission capacity without causing new problems such as an increase in size, and can effectively function the inertial mass body as a flywheel. An object is to provide a flywheel device with a damper mechanism.
[0012]
[Means for Solving the Problems]
According to a first aspect of the present invention, there is provided a damper mechanism in which a driving member for transmitting an input torque and an inertial mass body are connected to each other in the rotational direction via an elastic member, and a friction that enables frictional engagement between the driving member and the inertial mass body. In the flywheel device with a damper mechanism having an engagement means, the inertial mass body includes a first holding body and a second holding body that hold the elastic member and are integrated in a rotation direction. In addition, the elastic member, the first holding body, and the second holding body are coupled so as to be relatively movable in the axial direction, and a plurality of the driving member and the first and second holding bodies are combined. The flywheel device with a damper mechanism is characterized in that a plurality of the friction engagement means frictionally engaged between members are configured.
Further, the invention of claim 2, wherein the first holding member definitive to claim 1 and said second holding member is, the driving member that is engaged with the elastic member sandwiched and mutually axially The friction engagement means are arranged so as to approach and separate from each other, and the friction engagement means includes a friction surface that contacts the first holding body and the driving member, and a friction surface that contacts the second holding body and the driving member. A flywheel device with a damper mechanism.
The invention of claim 3, in claim 1 Ah Rui 2 of the invention, together with the drive member further has a movably engaged cover against integrated and axial direction with respect to the rotation direction The first holding body is disposed between the inner surface of the cover and the driving member so as to be movable in the axial direction, and the friction engagement means is in contact with the driving member and the first holding body. The flywheel device with a damper mechanism includes a friction surface and a friction surface between the first holding body and the inner surface of the cover.
[0013]
That is, according to the present invention, since a plurality of friction engagement means for enabling frictional engagement between the drive member for transmitting the input torque and the inertial mass body are provided, the friction engagement portion is increased, and the torque transmission is accordingly performed. As the capacity increases, the inertial mass can effectively function as a flywheel. Further, at that time, new problems such as an increase in the size of the apparatus and an increase in hydraulic pressure do not occur.
[0014]
The concept of “providing a plurality of friction engagement means” includes a case in which a friction engagement surface is formed at a plurality of locations between the same member, and a case in which a plurality of friction engagement surfaces are formed between a plurality of members. Both are included.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
In a preferred embodiment of the present invention, the elastic member and the first holding body and the second holding body that hold the elastic member are coupled so as to be movable relative to each other in the axial direction, and the friction engagement means includes the drive It is set as the structure friction-engaged between several members with a member and the said 1st and 2nd holding body. As a result, the torque transmission capacity can be increased, that is, the function of the inertia mass body as a flywheel can be improved only by a simple structural change.
[0016]
Hereinafter, examples of more specific embodiments of the present invention will be described in detail with reference to the drawings.
[0017]
FIG. 1 shows a hydraulic clutch device including a flywheel device with a damper mechanism according to a first embodiment of the present invention.
[0018]
In this hydraulic clutch device, a housing 105 is formed by a front cover 102 and an outer shell 103 integrated with the front cover 102 by welding, and a clutch 110 and a damper mechanism 112 are provided therein. The damper mechanism 112 is disposed between the clutch 110 and the front cover 102. The damper mechanism 112 sandwiches the spring location (drive member) 116 and the spring location 116, and at the same time, the first damper spring (elasticity). A member) 118 mainly includes an inner plate (first holding body as an inertial mass body) 122 and a spring holding cover (second holding body) 124.
[0019]
The inner plate 122 and the spring holding cover 124 are annular plate-like members, and both are integrated in the rotational direction, but are movable in the axial direction (left-right direction in the figure) X. FIG. 2 is a cross-sectional view showing the upper half of the inner plate, and FIG. 3 is a front view showing a quarter portion of the inner plate as viewed from the direction III in FIG. 4 is a cross-sectional view of the upper half of the spring holding cover 124, and FIG. 5 is a front view showing a ¼ portion of the spring holding cover 124 viewed from the direction V in FIG. The recess 122 ′ of the inner plate 122 shown in FIG. 3 and the protrusion 124 ′ of the spring holding cover 124 shown in FIG. Further, after the inner plate 122 and the spring holding cover 124 are combined, as shown in FIG. 6, an enlarged view of the portion indicated by the symbol R in FIG. I am trying.
[0020]
Returning to FIG. 1, the distance d2 between the surface 126 of the inner plate 122 and the front cover 102 is set to be larger than the distance d1 between the surface 124b of the spring holding cover 124 and the front cover 102.
[0021]
According to the conventional technical idea, as is apparent from the comparison with FIG. 12, the inner plate 122 and the spring holding cover 124 are fixed by welding at the portion indicated by the reference sign Q in FIG. For this reason, only one surface of the inner plate 122 and the front cover 102 is engaged with the front cover 102 to transmit torque.
[0022]
On the other hand, in this embodiment, the surface 124b of the spring holding cover 124 is engaged with the front cover 102 as a first friction surface, and the surface 124a of the spring holding cover 124 and the surface 122a of the inner plate 122 are respectively second and As a third friction surface, the spring location 116 is engaged from both sides. That is, friction engagement means is formed between the members of the front cover 102 and the spring holding cover 124, between the members of the spring holding cover 124 and the spring location 116, and between the members of the spring location 116 and the inner plate 112. In this way, three surfaces are used as friction surfaces. As a result, the torque capacity can be greatly increased.
[0023]
The spring location 116 engages with the outer shell 103 at the outer peripheral portion, and is slightly movable in the axial direction X with respect to the front cover 102, and is integrated in the rotation direction and rotates in the same direction.
[0024]
Further, the spring location 116 pushes the first damper spring 118 in the rotation direction, so that the inner plate 122 and the spring holding cover 124 holding the first damper spring 118 also rotate in the same direction.
[0025]
The clutch 110 is connected to the inner plate 122 so as to be engaged and disengageable, and transmits torque transmitted from the engine side through the front cover 102 to the output shaft (input shaft of the automatic transmission) 130 side. Shut off (connect).
[0026]
The clutch 110 mainly includes a piston chamber 132, a piston 134, a pair of pressure plates 136a, 136b, and a disk 138 disposed between the pair of pressure plates 136a, 136b.
[0027]
The piston 134 can slide in the axial direction X by a differential pressure (p1-p0) between the hydraulic pressure p1 introduced into the piston chamber 132 (on one side thereof) and the hydraulic pressure p0 introduced into the space 140 (on the other side). It is. Since the pair of pressure plates 136a and 136b is restricted from moving in the axial direction X by the stop ring 142, when pressed on one side by the piston 134, the disk 138 disposed therebetween is strongly held. Further, when the pressing of the piston 134 is stopped, the piston 134 moves away from the disk 138.
[0028]
Each of the pressure plates 136a and 136b can move in the axial direction X, but the peripheral portion in the radial direction is engaged with and fixed to the inner plate 122 in the rotational direction, and is rotated integrally with the inner plate 122. . Friction plates 128 a and 128 b are disposed on the disk 138, and the connection and disconnection of power from the engine side is realized by the pressure plates 136 a and 136 b being sandwiched and separated from the disk 138.
[0029]
The disc 138 of the clutch 110 is connected to the second damper spring 144, and the second damper spring 144 is connected to the output shaft 130 via the spring holding covers 146 a and 146 b and the hub 114.
[0030]
On the other hand, a piston chamber 150 into which the hydraulic pressure p <b> 1 is introduced is formed between the front cover 102 and the inner plate 122, and the inner plate 122 is movable along the output shaft 130.
[0031]
The space 140 is connected to an oil passage 152, and the piston chambers 132 and 150 are connected to an oil passage 154.
[0032]
Next, the operation of the first embodiment will be described.
[0033]
First, the case where the clutch 110 is in the released state will be described.
[0034]
When releasing the clutch 110, oil is supplied from the oil passage 152, and a high hydraulic pressure p 0 is generated in the space 140. The piston chambers 132 and 150 generate a hydraulic pressure p1 close to zero (very weak).
[0035]
As a result, a hydraulic pressure difference p0-p1 is generated on both sides in the axial direction X of the piston 134 of the clutch 110, so that the piston 134 moves to the right in the figure, and the pressure plates 136a, 136b are separated from the disk 138. As a result, the clutch 110 is released.
[0036]
On the other hand, due to the hydraulic pressure difference (p0> p1) generated on the left side of the piston 134 and the right side of the inner plate 122 in FIG. 1, the diameter of the portion where the inner plate 122 receives the hydraulic pressure from the piston chamber 150 as shown in FIG. , F = (π / 4) × Do ² × (p0−p1), and the piston 134 and the inner plate 122 integrally move in the right direction in the figure. The inner plate 122 presses the spring location 116 in the right direction in the figure through the friction surface 122a, and the spring location 116 presses the spring holding cover 124 toward the front cover 102. That is, the front cover 102 and the inner plate (inertial mass body) 122 are integrated via the three friction surfaces (122a, 124a, 124b) by the hydraulic pressures p0, p1 for releasing the clutch 110.
[0037]
Next, the case where the clutch 110 is in an engaged state will be described.
[0038]
When the clutch 110 is engaged, a high hydraulic pressure p <b> 1 is supplied to the piston chambers 132 and 150 through the oil passage 154. At this time, the hydraulic pressure p0 supplied to the space 140 is set to a pressure close to zero. When the hydraulic pressure p1 supplied to the piston chambers 132 and 150 is higher than the hydraulic pressure p0 on the space 140 side, a hydraulic pressure difference p1−p0 is generated on both sides of the piston 134 of the clutch 110. The inner plate 122 and the stop ring 142 are integrated, and the axial distance between the both 122 and 142 is not changed. Therefore, due to the hydraulic pressure difference p1-p0, the piston 134 moves in the left direction in the figure, so that the pressure plates 136a, 136b receive the reaction force of the stop ring 142 and strongly hold the disc 138. As a result, the clutch 110 is engaged.
[0039]
In FIG. 1, a high hydraulic pressure p <b> 1 is applied to the right side of the inner plate 122, and a low hydraulic pressure p <b> 0 is applied to the left side of the piston 134. Accordingly, the inner plate 122 and the piston 134 move in the left direction in the drawing as a whole. As a result, the (friction) surface 124b is separated from the front cover 102 and the rightward force is released, so that the coupling force between the (friction) surfaces 124a and 122a and the spring location 116 is lost, and the inner plate 122 is (Friction) It becomes possible to solve the integration through the surfaces 122a, 124a, and 124b. On the other hand, since the first damper spring 118 sticks to the outer diameter side due to centrifugal force or the like, the inner plate 122 and the spring holding cover 124 are moved and fixed to a position where the stopper 125 shown in FIG.
[0040]
Therefore, the front cover 102 and the inner plate 122 are connected via the first damper spring 118, and the engine-side torque fluctuation can be satisfactorily absorbed.
[0041]
As described above, according to the present embodiment, the number of friction surfaces is increased and the position is set near the outer diameter side, so that the torque transmission capacity is greatly increased, and the inner plate (inertial mass body) ) 122 can effectively function as a flywheel. Therefore, quietness at the time of idling is improved. In addition, since the torque transmission capacity can be secured even if the diameter D of the piston chamber 150 is reduced, the bearings B1 and B2 can be made easier and the size can be reduced.
[0042]
Next, a second embodiment of the present invention will be described.
[0043]
FIG. 7 shows a torque converter having a flywheel device with a damper mechanism according to the second embodiment.
[0044]
In FIG. 7, the torque converter 201 includes a pump 204 that rotates integrally with the front cover 202, and a turbine 206 that is rotated (via the fluid) by the rotation of the pump 204. In addition, a stator 208 is disposed in an inner peripheral portion between the pump 204 and the turbine 206. The turbine 206 is connected to the hub 214 so as to be rotatable integrally with the hub 214, and power is transmitted to an output shaft (not shown) (input shaft of the automatic transmission) via the hub 214.
[0045]
A lockup clutch 210 and a damper mechanism 212 are provided between the inner surface of the front cover 202 and the turbine 206. The lock-up clutch 210 engages with the hub 214 on the inner peripheral side and is integrated in the rotation direction, but is slidable in the axial direction (left-right direction in the figure) X.
[0046]
The configuration of the outer periphery of the damper mechanism 212 is the same as in the first embodiment. That is, the damper mechanism 212 is disposed between the lockup piston 210 a of the lockup clutch 210 and the front cover 202, and the damper mechanism 212 sandwiches the spring location (drive member) 216 and the spring location 216. At the same time, an inner plate (first holding body as an inertial mass body) 222 that holds the first damper spring (elastic member) 218 and a spring holding cover (second holding body) 224 are mainly configured. .
[0047]
A friction material 228 is affixed to a surface of the lockup piston 210a that faces the inner plate 222 at the periphery thereof, and comes into contact with the inner plate 222 so that the clutch is engaged.
[0048]
The inner plate 222 and the spring holding cover 224 hold the second damper spring 260 on the inner peripheral side from the first damper spring 218, and are coupled by a rivet 223 between the first damper spring 218 and the second damper spring 260. Yes. This coupling is not fixed, and as shown in an enlarged view in FIG. 8, a gap d3 is provided between the inner plate 222 and the spring holding cover 224, and the spring holding cover 224 is movable in the axial direction X. It is said that.
[0049]
The spring location 216 engages with the outer shell 203 and is movable in the axial direction X, but the rotational direction is fixed. As already described with reference to FIG. 12, the conventional friction engagement means is only one of the friction surfaces 226 (26) of the inner plate 222 (22). However, in the present embodiment, as shown in the enlarged view of FIG. 9, the inner plate 222, the spring location 216, and the spring holding cover 224 can move in the axial direction X, and the friction surface 226, the spring Each of the friction surfaces 224 a and 224 b of the holding cover 224 can contact the spring location 216 and the front cover 202. That is, three friction engagement means are provided.
[0050]
As shown in FIG. 9, the distance L1 between the spring holding cover 224 and the front cover 202 is set to be smaller than the distance (backlash) L2 between the spring location 216 and the front cover 202. Accordingly, the friction surface 224a and the spring location 216, and the friction surface 224b and the front cover 202 can be reliably in contact with each other.
[0051]
Hereinafter, the operation of the second embodiment will be described.
[0052]
When releasing the lock-up clutch 210, in FIG. 7, oil is supplied from the portion indicated by G as indicated by an arrow, and the pressure is discharged from the portion indicated by H (as opposed to the arrow). As a result, the hydraulic pressure between the lock-up piston 210a and the inner plate 222 increases, and the lock-up piston 210a is separated from the inner plate 222. Therefore, the lock-up clutch 210 is released, and torque is transmitted through the oil by the function of the normal torque converter 201.
[0053]
On the other hand, due to the high hydraulic pressure between the inner plate 222 and the lock-up piston 210a, the inner plate 222 is pressed to the left in the figure, the friction surface 226 hits the spring location 216, and the inner plate 222, the spring location 216, the first damper spring. 218 and the spring holding cover 224 move together to the left. As a result, the friction surfaces 224a and 224b of the spring holding cover 224 come into contact with the front cover 202 and the spring location 216, respectively. As described above, since the spring holding cover 224 is not fixed in the rivet 223 and is movable in the axial direction X, the friction surfaces 224a and 224b are reliably contacted.
[0054]
In this embodiment, since the number of friction engagement means (friction surfaces 226, 224a, 224b) is increased, the torque transmission capacity is increased, and the function of the inertia mass body as a flywheel can be improved.
[0055]
Next, when the lock-up clutch 210 is engaged, the hydraulic pressure is supplied in the direction of the arrow from the portion H in FIG. 7 and discharged from the portion G (opposite to the arrow) in FIG. As a result, the back side (right side in the figure) of the lockup piston 210a becomes high pressure and the front side (left side) becomes low pressure, and the lockup piston 210a is moved to the damper mechanism 212 side. At this time, since the hydraulic pressure between the inner plate 222 and the lock-up piston 210a is lowered, the inner plate 222 moves to the right side (lock-up piston 210a side) in the figure, and the friction material 218 attached to the lock-up piston 210a is moved to the inner side. The clutch 222 is pressed against the plate 222. However, the friction surfaces 226, 224 a and 224 b are not engaged, and torque is transmitted from the front cover 202 to the lockup clutch 210 via the spring location 216, the first damper spring 218 and the inner plate 222. Therefore, the damper mechanism 212 literally acts as a damper.
[0056]
As for the shape of the engaging portion between the spring location 216 and the outer shell 203 and the shape of the rivet 223, the structure described above is simple in structure and easy to manufacture, but is not limited thereto. Various other structures are conceivable.
[0057]
For example, the engaging portion between the spring location 216 and the outer shell 203 is provided with an elastomer 264 at the end of the front cover 202 as shown in FIG. 10, and a distance L 2 ′ between the elastomer 264 and the spring location 216. By satisfying L2>L1> L2 ′, the spring location 216 may be returned smoothly (to the right in the drawing) when the friction surface 224b is disengaged.
[0058]
Further, for the rivet 223 portion, for example, as shown in FIG. 11, a coil spring 266 may be provided to secure a gap so that the friction surfaces 224a and 226 are not engaged except when necessary. .
[0059]
【The invention's effect】
As described above, according to the present invention, the torque transmission capacity can be increased by using a plurality of friction engagement means, and the function of the inertia mass body as a flywheel can be improved.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing a flywheel device with a damper mechanism according to a first embodiment of the present invention. FIG. 2 is a sectional view of an upper half showing the shape of an inner plate in the first embodiment. Fig. 4 is a front view showing a quarter portion seen from the III direction. Fig. 4 is a sectional view of the upper half showing the shape of the spring holding cover in the first embodiment. Fig. 6 is a front view showing a portion 4; Fig. 6 is an enlarged view of a portion R in Fig. 1. Fig. 7 is a longitudinal sectional view showing a flywheel device with a damper mechanism according to a second embodiment of the invention. Fig. 9 is an enlarged view of the rivet 223 portion in Fig. 9. Fig. 9 is an enlarged view of the vicinity of the engaging portion between the spring location and the outer shell in Fig. 7. Fig. 10 is an enlarged view showing another example of the engaging portion between the spring location and the outer shell. FIG. 11 is a cross-sectional view of the rivet 223 in FIG. Fig. 12 is an enlarged sectional view showing another example of the portion. Fig. 12 is a longitudinal sectional view showing a conventional flywheel device with a damper mechanism.
102, 202 ... front cover 103, 203 ... outer shell 110 ... clutch 112, 212 ... damper mechanism 116, 216 ... spring location (drive member)
118, 218 ... first damper spring (elastic member)
122, 222 ... Inner plate (inertial mass body, first holding body)
124, 224 ... Spring holding cover (second holding body)
122a, 222a, 124a,
224a, 124b, 224b, 126, 226 ... friction surface 128, 228 ... friction material 210 ... lock-up clutch 210a ... lock-up piston

Claims (3)

A damper having a damper mechanism in which a driving member for transmitting input torque and an inertial mass body are coupled in a rotational direction via an elastic member, and a friction engagement means for enabling frictional engagement between the driving member and the inertial mass body. In the flywheel device with mechanism,
The inertial mass body is constituted by a first holding body and a second holding body that hold the elastic member and are integrated in a rotation direction, and the elastic member, the first holding body, A plurality of friction engagements coupled to the second holding body so as to be relatively movable in the axial direction, and further frictionally engaged between a plurality of members of the drive member and the first and second holding bodies. means flywheel device with a damper mechanism which is characterized that you are configured. The first holding body and the second holding body are disposed so as to sandwich the drive member engaged with the elastic member and to approach and separate from each other in the axial direction. 2. The structure according to claim 1, further comprising a friction surface that contacts the first holding body and the driving member and a friction surface that contacts the second holding body and the driving member. Flywheel device with damper mechanism. The drive member further includes a cover that is integrated with respect to the rotation direction and is movably engaged with respect to the axial direction, and the first holding body is disposed between the inner surface of the cover and the drive member. The friction engagement means is arranged to be movable in the axial direction, and the friction engagement means includes a friction surface that contacts the driving member and the first holding body, and a friction surface that contacts the first holding body and the inner surface of the cover. The flywheel device with a damper mechanism according to claim 1, wherein the flywheel device includes a damper mechanism.

Images