JP2004257506A - Torque converter with lock-up clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque converter with a lockup clutch capable of reliably controlling engagement/disengagement of a stator by a simple structure while omitting a one-way clutch of a stator by using the control hydraulic pressure of the lock-up clutch. <P>SOLUTION: In the torque converter with the lock-up clutch, an annular supporting member to support a stator and an annular non-rotating member facing the supporting member and provided in a non-rotating manner are provided. The supporting member and the non-rotating member are engaged with each other in response to the first flow to generate the lock-up releasing pressure to separate a piston from a cover member, and disengaged from each other in response to the second flow to generate the lock-up pressure to bring the piston into contact with the cover member. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a torque converter device with a lock-up clutch for an automobile or the like, and more particularly, to a torque converter device with a lock-up clutch provided with a lock mechanism for a stator.
[0002]
[Prior art]
Usually, the automatic transmission includes a torque converter, and transmits the rotation of the engine output to the crankshaft to the input shaft of the transmission via the torque converter. This torque converter includes a pump impeller, a turbine runner, a stator, and the like, and generally includes a lock-up clutch device and a damper device.
[0003]
In such a torque converter, when the speed ratio (turbine rotation speed / pump rotation speed) falls within a predetermined range, the flow of the fluid in the torque converter hits the back surface of the stator impeller, and the efficiency drops rapidly. I do. Therefore, in order to prevent such a decrease in efficiency, the stator is generally connected to an appropriate non-rotating member via a one-way clutch that locks rotation in the same direction with respect to the pump and the turbine and locks rotation in the opposite direction. ing.
[0004]
In this one-way clutch, the difference in rotation speed between the pump and the turbine with respect to the stator described above is large, and in the converter region where the fluid flows on the surface side of the stator impeller, the flow of fluid returning from the turbine to the pump is controlled by the impeller. In the coupling area where the deflection on the surface side amplifies the torque of the turbine by amplifying the torque of the turbine, the difference in the number of revolutions between the pump and the turbine is small, and the fluid flow hits the back side of the stator impeller, the rotation direction of the pump and the turbine In the same direction as above, it acts to prevent loss of flow.
[0005]
The one-way clutch that operates as described above adopts a configuration in which a number of radial engagement members (sprags and the like) are arranged while maintaining a circumferential interval between the inner race and the outer race by a spacing member. The structure is complicated, the number of parts is large, and heat treatment such as quenching of the engagement surface between the inner and outer races is required to ensure the precision machining of the engagement surface and the durability. It was difficult to reduce the cost.
[0006]
Therefore, a torque converter including a stator without such a one-way clutch has been proposed.
[0007]
For example, there has been proposed a torque converter with a lock-up clutch in which engagement between a stator and a non-rotating member is performed by axially moving the stator by a thrust force acting on the stator or the turbine hub by a flow in the torus. (For example, see Patent Document 1).
[0008]
Patent documents 2 and 3 listed below are relevant to such techniques.
[0009]
[Patent Document 1]
JP-A-2002-195375
[Patent Document 2]
JP-A-08-42685
[Patent Document 3]
JP 2001-241532 A
[0010]
[Problems to be solved by the invention]
However, in the torque converter device with a lock-up clutch disclosed in Patent Document 1 described above, the engagement / disengagement of the stator engagement portion is controlled by using the thrust force. There is a possibility that the engagement and controllability of the steel may decrease. That is, it is difficult to control the thrust force, and the controllability of engagement between the stator and the non-rotating member may be reduced.
[0011]
In view of the above-mentioned problems of the prior art, the present invention uses a control hydraulic pressure of a lock-up clutch to omit the one-way clutch of the stator, and more reliably engages and disengages the stator with a simple structure. It is an object of the present invention to provide a torque converter device with a lock-up clutch capable of controlling the torque converter.
[0012]
[Means for Solving the Problems]
To achieve the above object, a torque converter device with a lock-up clutch according to the present invention includes a pump impeller connected to an engine output shaft via a cover member, and a transmission input shaft disposed opposite to the pump impeller. And a stator disposed between the pump impeller and the turbine runner, and an annular piston disposed between the cover member and the turbine runner and movable in the axial direction. A lock-up clutch, and a torque converter device with a lock-up clutch, comprising: an annular support member that supports the stator; and an annular non-rotating member that is non-rotatably opposed to the support member. The support member and the non-rotating member are unlocked to separate the piston from the cover member. It is configured to be engaged in response to a first flow that produces a force and released in response to a second flow that produces a lock-up pressure that causes the piston to contact the cover member. It is characterized by the following.
[0013]
In the torque converter device with a lock-up clutch of the present invention configured as described above, an annular support member that supports the stator and an annular non-rotating member that is non-rotatably provided facing the support member are provided. The member and the non-rotating member are engaged in response to a first flow that creates a lock-up release pressure that separates the piston from the cover member, creating a lock-up pressure that causes the piston to contact the cover member. It is configured to be released in response to the second flow, so the end bearing is required and the cost is increased.The conventional complicated one-way clutch is omitted, and the stator is more reliably configured with a simple structure. Can be controlled to be engaged and disengaged.
[0014]
In addition, a flow path that forms the first flow and the second flow, a communication path introduced into a pressure chamber formed between the support member and the non-rotating member, An opening communicating with a communication passage, wherein the opening is provided downstream of the first flow near the support member and the non-rotating member.
[0015]
In this case, when the lock-up is OFF, the hydraulic oil flows up through the pump impeller, the turbine runner, and the stator by rising from between the cover member and the lock-up piston and driving the lock-up piston away from the cover member. And the pressure chamber formed between the non-rotating member and the supporting member are communicated on the downstream side, so that the pressure chamber formed between the non-rotating member and the supporting member due to pressure loss due to fluid resistance. Is lower than the pressure around the non-rotating member and the supporting member, and a force is generated in a direction in which the non-rotating member and the supporting member engage, thereby fixing the stator. On the other hand, when the lock-up is ON, almost no flow occurs around the stator, so that the above-described engagement force is released, and the stator becomes rotatable. This makes it possible to realize a function equivalent to that of a conventional one-way clutch.
[0016]
Furthermore, the flow path near the opening may be formed in a narrow path.
[0017]
In this case, since the flow path in the vicinity of the opening is narrowed, the flow velocity in this portion is increased, thereby reducing the pressure, and the pressure generated in the space formed by the non-rotating member and the support member, The differential pressure generated between the non-rotating member and the pressure generated around the support member becomes larger, and the engagement force can be promoted.
[0018]
Further, an elastic member is provided between the piston and the cover member for generating an urging force to separate the piston from the cover member in the axial direction, and the support member and the non-rotating member include The urging force may be promoted by one flow to be engaged, and released by the second flow against the urging force.
[0019]
In this case, at the time of lock-up OFF, the lock-up piston urged by the elastic member in the lock-up OFF direction moves the support member of the stator constituting the engagement means to the non-rotating member via a member movable in the axial direction. Energize in the direction of engagement. Thereby, the support member and the non-rotating member are engaged with each other with the aid of the elastic force of the elastic member, and the stator is fixed, and the release performance of the lock-up piston and the cover member when lock-up is OFF is also improved. . On the other hand, when the lock-up is ON, the lock-up piston lock-engages with the cover member due to an oil pressure greater than the elastic force of the elastic member, and the engaging force between the support member and the non-rotating member is released, and the stator is turned off. It becomes rotatable.
[0020]
Further, the piston is liquid-tightly sealed and supported movably in the axial direction on an outer peripheral end face and an inner peripheral end face, and the support member and the non-rotating member are configured to support the first flow and the second flow. The engagement / disengagement may be performed in conjunction with the axial movement of the piston due to the second flow.
[0021]
In this case, the operating oil pressure during lock-up ON and OFF can be more effectively applied to the lock-up piston, and efficient lock-up ON / OFF control can be performed.
[0022]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0023]
First, an outline of a torque converter to which the present invention is applied will be described with reference to FIG.
[0024]
FIG. 1 is a sectional view showing an upper half of a torque converter with a lock-up clutch according to a first embodiment of the present invention.
[0025]
As shown in FIG. 1, the torque converter 1 includes a converter cover 12, a pump impeller 13, a turbine runner 14, a turbine hub 15, a stator 30, a lock-up clutch mechanism 17, which are rotatably arranged around the same rotation axis. And a damper 19 and the like.
[0026]
In the torque converter 1 configured as described above, the torque transmitted from the engine (not shown) is transmitted to the pump impeller 13 via the converter cover 12, and the torque is generated by the flow of hydraulic oil generated with the rotation of the pump impeller 13. The turbine runner 14 is rotated, and the rotation of the turbine runner 14 is transmitted to the input shaft 100 of the transmission 5 via the turbine hub 15.
[0027]
Here, hydraulic oil is supplied from an oil pump (not shown) provided on the transmission 5 side to an inner surface of the converter cover 12 through an oil passage 102 provided inside the input shaft 100 of the transmission 5. Flows through the space formed by the side surface of the lock-up piston 20 facing the outer periphery of the lock-up piston 20, passes through the inside of the torus, further extends from the transmission case, and the converter. When the oil flows back to the oil pump via the flow path 52 formed between the cover support member 60 and the inner peripheral portion of the cover support member 60 connected to the cover 12, the lock-up piston 20 , And is kept in the lock-up OFF state. Since the bush 55 is arranged in the space 54 formed between the input shaft 100 and the sleeve 50, almost no flow occurs.
[0028]
On the other hand, when the flow of the hydraulic oil in the opposite direction to the above-described flow is formed via the switching valve, the lock-up piston 20 is pressed in the axial direction so as to contact the converter cover 12, The lock-up ON state is maintained. That is, when the vehicle speed reaches a predetermined speed after the start of the vehicle, the lock-up piston 20 is provided on the outer peripheral portion of the lock-up clutch mechanism 17 by the pressure of the hydraulic oil sent from the oil pump via the flow path 52. The clutch member 18 pressed against the inner surface of the converter cover 12 causes the power transmitted from the engine (not shown) to the converter cover 12 to be directly transmitted to the turbine hub 15 as an output member, and the engine and the transmission 5 Is directly connected to the input shaft 100.
[0029]
The damper 19 interposed between the lock-up piston 20 on the input side and the turbine hub 15 on the output side absorbs fluctuations in torque transmitted from the converter cover 12 to the turbine hub 15 when the lock-up is ON. Will be done.
[0030]
Next, the engagement means of the stator according to the first embodiment of the present invention will be described in detail.
[0031]
As shown in FIG. 1, the pump impeller 13, the turbine runner 14, the lock-up clutch mechanism 17 and the like are arranged in a space formed by the converter cover 12 connected to the rotatable cover support member 60. I have. An annular non-rotating member 40 having a boss 40L partially fits tightly on a sleeve 50 extending from the transmission case around the input shaft 100 having an oil passage 102 for hydraulic oil, and cannot rotate. , And is supported in the axial direction via a bearing 37 provided on the converter cover 12. The first inner peripheral portion 33a is supported by the outer peripheral portion of the non-rotating member 40, and the second inner peripheral portion 33b is supported by the boss portion 40L so as to be slidable in the axial direction. An annular support member 33 to which the stator 30 is attached is disposed. The support member 33 is axially supported via a bearing 35 provided on a side surface of the turbine hub 15.
[0032]
Here, a friction member 33 d extending in the radial direction of the rotation shaft is provided on a side surface 33 c of the support member 33 facing the side surface 40 a of the non-rotation member 40, and the friction member 33 d is opposed to the opposite surface 40 a of the non-rotation member 40. An engaging means is formed between them.
[0033]
Further, for example, a seal ring is interposed on the outer peripheral portion of the non-rotating member 40, and the boss 40 </ b> L of the non-rotating member 40 on the side facing the second inner peripheral portion 33 b of the support member 33, for example, A seal ring is interposed and forms 43a and 43b, respectively. A seal portion 43s is formed by the above-mentioned close fitting portion between the non-rotating member 40 and the sleeve 50. Thus, a pressure chamber SL, which is a substantially closed space, is formed between the side surface of the support member 33 on the friction member 33d side and the side surface 40a of the non-rotating member 40 opposed thereto.
[0034]
The seal portion 43s may be formed by, for example, interposing a seal ring similar to the seal portions 43a and 43b described above.
[0035]
Further, the non-rotating member 40 is formed on the transmission 5 side thereof with a bypass passage 41 for bypassing the flow of hydraulic oil around the bearing 37, and a side surface of the supporting member 33 facing the friction member 33d. A communication passage 44 communicating with the pressure chamber SL is formed from the radial center toward the inner peripheral side where the above-mentioned seal portion 43s is formed. The communication passage 44 is communicated with a communication passage 46 formed inside the sleeve 50. The communication passage 46 is connected to the above-described passage 52 which is a passage for driving the lock-up piston 20. 50 are communicated via an opening 45 provided on the outer peripheral surface.
[0036]
Here, the friction member 33d may have a multi-plate structure corresponding to the load of the stator 30, and a frictional surface of the friction member 33d is formed with, for example, a lattice-shaped groove for appropriately applying hydraulic pressure. be able to.
[0037]
Next, the operation of the thus configured stator 30 of the torque converter according to the first embodiment of the present invention will be described with reference to FIG.
[0038]
FIG. 2 is a diagram illustrating the flow of the hydraulic oil when the lockup is turned off. In FIG. 2, the solid arrow indicates the main flow of the hydraulic oil having a large flow rate, and the dotted arrow indicates the flow having a small flow rate (almost no flow).
[0039]
At the time of lock-up OFF in which the first flow is formed, as shown in FIG. 2, hydraulic oil for driving the lock-up piston 20 is supplied from an oil pump (not shown) provided at The space formed by the inner surface of the converter cover 12 and the side surface of the lockup piston 20 facing the converter cover 12 is locked up through the illustrated switching valve and the oil passage 102 provided inside the input shaft 100. It flows toward the outer peripheral side of the piston 20. Then, while pressing the lock-up piston 20 so as to separate the lock-up piston 20 from the converter cover 12 in the axial direction, the lock-up piston 20 flows through the outer periphery of the lock-up clutch mechanism 17 into the torus. After passing through the space on the side, the air passes through the bypass flow path 41 and the flow path 52 provided in the non-rotating member 40 and returns to the transmission 5 side.
[0040]
Due to such fluid resistance of the flow of the hydraulic oil, a pressure loss occurs, and the pressure around the opening 45 becomes the pressure of the space SH around the support member 33 and the non-rotating member 40 located upstream of the opening 45. Lower than. On the other hand, the pressure in the pressure chamber SL, which is substantially sealed by the seal portions 43a and 43b, is substantially the same as the pressure around the opening 45 because there is no flow of the fluid, and the support member 33 and the non-rotating member 40 The pressure becomes lower than the pressure in the surrounding space SH.
[0041]
Therefore, the flow of the hydraulic oil driving the lock-up piston 20 to the lock-up OFF state attracts each other between the friction member 33 d provided on the support member 33 of the stator 30 and the opposed side surface 40 a of the non-rotating member 40. The force in the direction acts, the friction member 33d of the support member 33 and the opposing surface 40a of the non-rotating member 40 engage, and the stator 30 is fixed so as not to rotate.
[0042]
Here, if the flow path 52 around the opening 45 is formed as a narrow path (throttle), the flow velocity of the hydraulic oil around the opening 45 becomes faster. Then, with the increase in the flow velocity, the pressure drop around the opening 45 is promoted, the differential pressure generated between the space SH and the pressure chamber SL increases, and the frictional member 33d and the opposing surface 40a are in contact with each other. A larger engagement force can be obtained between them.
[0043]
On the other hand, when the state changes from the lock-up OFF state to the lock-up ON state that forms the second flow, the hydraulic oil that drives the lock-up piston 20 transiently changes during the lock-up OFF state. As described above, the pump impeller 13 of the stator 30 passes through the flow path 52 from the oil pump via the switching valve and the bypass impeller 41 provided in the non-rotating member 40 in a direction opposite to the flow of the hydraulic oil. From the space on the side to the space formed between the pump impeller 13 and the turbine runner 14. The flow of the hydraulic oil presses the lock-up piston 20 so that the clutch member 18 comes into contact with the inner surface of the converter cover 12. After the lock-up ON state in which the inner surface of the converter 12 is in contact with the lock-up piston 20, the clutch member 18, and the inner peripheral surface of the converter cover 12, a seal portion is formed. Flow is interrupted. As a result, almost no flow occurs in the space SH around the support member 33 and the non-rotating member 40, and the pressure is almost the same as the pressure around the opening 45. Therefore, the pressure in the pressure chamber SL communicated with the opening 45 is also substantially the same, so that the side surface having the friction member 33d provided on the support member 33 of the stator 30 and the facing surface 40a of the non-rotating member 40 The forces in the directions of attracting each other generated between the two disappear, and the stator 30 can freely rotate.
[0044]
The timing of switching the stator 30 from the fixed state (so-called converter state) to the rotatable state (so-called coupling state) is almost the same as the timing of switching the lock-up clutch mechanism 17 from the lock-up OFF state to the lock-up ON state. Therefore, the stator 30 of the torque converter 1 according to the present invention configured as described above can realize substantially the same function as a conventional stator with a one-way clutch.
[0045]
Normally, a stator with a one-way clutch is fixed so as not to rotate when the lock-up is OFF, for example, when the rotation speed difference between the pump impeller and the turbine runner is large, and when the lock-up is ON, for example, the rotation speed difference between the pump impeller and the turbine runner. When is small, it is rotatable.
[0046]
In the stator 30 of the torque converter 1 according to the embodiment of the present invention, the one-way clutch is omitted and the flow of the hydraulic oil for driving the lock-up piston 20 is reduced as described above, which leads to an increase in cost such as the need for an end bearing. Utilizing the same function as a one-way clutch.
[0047]
In the present embodiment, for example, the flow of the hydraulic oil as shown in FIG. 2 is employed, but the flow is not limited thereto, and the space SH around the support member 33 and the non-rotating member 40 and the support member 33 The opening 45 for communicating the pressure chamber SL formed between the side surface 33c on the side of the friction member 33d and the side surface 40a of the non-rotating member 40 opposed thereto is actuated when the lock-up is OFF compared to the space SH. The same function can be realized by providing it on the downstream side of the oil flow, that is, on the low pressure side.
[0048]
Further, the friction member 33d can be provided on both or one of the side surface 33c of the support member 33 on the friction member 33d side and the side surface 40a of the non-rotating member 40 opposed thereto.
[0049]
Further, in the present embodiment, the space SH and the pressure chamber SL are communicated with each other through the opening 45, and the stator 30 is driven by the pressure difference between the two. , The flow rate in the pressure chamber SL may be controlled independently by independently providing the flow paths 52 and 46.
[0050]
For example, a new dedicated flow path which is different from the oil path 102 and is not communicated with the flow path 52 is formed in the input shaft 100, and the dedicated flow path is communicated with the pressure chamber SL. If the flow rate control between the pressure chamber SL and the flow path 52 is performed independently, the flow rate control within the pressure chamber SL can be performed independently of the flow of the hydraulic oil in the flow path 52.
[0051]
In this case, the number of control elements and the number of flow paths are increased as compared with the first embodiment. However, since the fixing or rotation of the stator 30 can be freely set, the functions equivalent to those in the case of using the one-way clutch are completely equivalent. Can be realized. Further, by controlling the hydraulic pressure in the dedicated flow path to be lower, it is possible to set a variable capacity torque converter. As a result, when the input torque is large, it is expected that effects such as avoiding an increase in the load on the drive system, slowing down the behavior of the vehicle, and reducing engine noise can be obtained.
[0052]
Next, the engagement means of the stator according to the second embodiment of the present invention will be described with reference to FIG.
[0053]
In this embodiment, an elastic member 25 is provided between the inner peripheral side surface of the lock-up piston in the first embodiment and the converter cover 12 facing the inner peripheral side surface. Elements are the same as those in the first embodiment, and therefore, description thereof will be omitted for simplicity, and similar elements will be denoted by the same reference numerals.
[0054]
FIG. 3 is a sectional view showing an upper half of a torque converter 1A with a lock-up clutch according to a second embodiment of the present invention.
[0055]
In the present embodiment, as shown in FIG. 3, a lock-up piston is provided between a radial side surface near an inner peripheral side of a lock-up piston 20 which is an annular member and a side surface of the converter cover 12 opposed thereto. A disc spring 25 is provided as an elastic member that is biased so as to press the plate 20 toward the stator 30. The disc spring 25 is provided with an oil passage hole 26. Further, an inner peripheral end surface of the lock-up piston 20 is disposed in a concave portion 15a of the turbine hub 15 which is attached so as to be movable in the axial direction, and a contact surface 20a which is in contact with the concave portion 15a so as to press the concave portion 15a in the axial direction. Thus, the turbine hub 15 can be moved toward the stator 30 in the axial direction. Further, the turbine hub 15 axially supports the support member 33 of the stator 30 via the bearing 35 on the side surface on the stator 30 side as described above.
[0056]
In the present embodiment, the differential pressure generated between the space between the support member 33 and the non-rotating member 40 and the surrounding space as in the first embodiment is used as the driving force of the stator 30. Since they are not used, the seal portions 43a, 43b, 43s in the first embodiment become unnecessary.
[0057]
In the thus configured stator 30 of the torque converter 1A according to the second embodiment of the present invention, for example, as shown in FIG. When the motor 20 is driven to be separated from the converter cover 12, the hydraulic oil passes through an oil passage 102 provided inside the input shaft 100, and passes through an oil passage hole 26 provided in the disc spring 25. A flow similar to that of the first embodiment is formed along a space formed by the inner surface of the converter cover 12 and the side surface of the lockup piston 20 opposed thereto, and the lockup piston 20 is The elastic force of the disc spring 25 urged in the direction to separate from the disc 12 is applied to the disc spring 25 via the turbine hub 15 and the bearing 35. The friction member 33d provided on the support member 33 of the stator 30, and driven to engage the opposing surface 40a of the non-rotating member 40, the stator 30 is fixed. As a result, in addition to the driving force of the lock-up piston 20 due to the flow of hydraulic oil as in the previous embodiment, the elastic force of the disc spring 25 is also applied to the lock-up piston 20, so that the engagement force of the stator when the lock-up is OFF is performed. And the release performance of the lock-up piston 20 when the lock-up is OFF is also improved.
[0058]
On the other hand, when the lock-up piston 20 of the lock-up clutch mechanism 17 is driven to contact the converter cover 12 when the hydraulic oil is in the lock-up ON state, the lock-up is performed with a force larger than the urging force of the disc spring 25. The piston 20 makes the clutch member 18 provided on the outer periphery of the lock-up clutch mechanism 17 contact the converter cover 12, and the friction member 33 d provided on the support member 33 of the stator 30 and the opposing surface 40 a of the non-rotating member 40. Is released, whereby the stator 30 becomes rotatable.
[0059]
The contact surface 20a of the lock-up piston 20 may be set to a wider surface in order to stabilize the transmission of the urging force by the disc spring 25 and reduce the load on the members.
[0060]
Further, the friction member 33d provided on the support member 33 of the stator 30 may have a groove on the friction surface or a multi-plate structure, as in the first embodiment.
[0061]
Next, the engaging means of the stator according to the third embodiment of the present invention will be described with reference to FIG.
[0062]
In the present embodiment, the disc spring 25 in the second embodiment is omitted, and the outer peripheral end surface of the lock-up piston 20 is slidably sealed with the surface facing the converter cover 12. Since the basic components are the same as those of the second embodiment, the description is omitted for the sake of simplicity, and the same components are denoted by the same reference numerals.
[0063]
FIG. 4 is a sectional view showing an upper half of a torque converter 1B with a lock-up clutch according to a third embodiment of the present invention.
[0064]
In the present embodiment, as shown in FIG. 4, the inner peripheral side end face of the lock-up piston 20, which is an annular member, is, similarly to the second embodiment, mounted on a turbine hub 15 that is axially movable. The turbine hub 15 can be moved toward the stator 30 in the axial direction at the contact surface 20a which is disposed in the concave portion 15a and is in contact with the concave portion 15a so as to press the concave portion 15a in the axial direction. The support member 33 of the stator 30 is supported on the side surface of the turbine hub 15 on the stator 30 side via the bearing 35 so as to be movable in the axial direction as described above.
[0065]
Here, the inner peripheral end surface of the lock-up piston 20 is sealed by a seal portion 15 s provided between the lock-up piston 20 and an opposing surface of the concave portion 15 a of the turbine hub 15 which faces the lock-up piston 20. The outer peripheral end face is sealed movably in the axial direction by a seal portion 20s provided between the end face and the opposing face of the converter cover 12 facing the end face. A clutch member 22 is attached to a radial side surface of the lock-up piston 20 on the converter cover 12 side on the outer peripheral side.
[0066]
In the thus configured stator 30 of the torque converter 1B according to the third embodiment of the present invention, for example, as shown in FIG. When the drive oil 20 is driven to be separated from the converter cover 12, the hydraulic oil passes through an oil passage 102 provided inside the input shaft 100, and is opposed to the inner surface of the converter cover 12 and the outer peripheral end thereof. Is sealed by the seal portion 20s between the converter cover 12 and the inner peripheral end by the radial side surface of the lock-up piston 20 sealed between the seal portion 15s and the opposing surface of the recess 15a of the turbine hub 15. The lock-up piston 20 flows into the formed space, and is driven in a direction to separate the lock-up piston 20 from the converter cover 12. By moving the friction member 33d provided on the support member 33 of the stator 30 via the turbine hub 15 and the bearing 35 so as to engage with the opposing surface 40a of the non-rotating member 40, the stator 30 is fixed. You.
[0067]
On the other hand, when the lock-up piston 20 of the lock-up clutch mechanism 17 is driven to be in contact with the converter cover 12 when the hydraulic oil is in the lock-up ON state, the clutch provided on the outer peripheral side surface of the lock-up piston 20 The member 22 is brought into contact with the converter cover 12 and, in conjunction with the movement of the lock-up piston 20, between the friction member 33d provided on the support member 33 of the stator 30 and the opposing surface 40a of the non-rotating member 40. Is released, and the stator 30 becomes rotatable.
[0068]
In this way, since the inner peripheral side and the outer peripheral side of the lock-up piston 20 are sealed by the seal portions 15 s and 20 s, the driving pressure for driving the lock-up piston 20 by hydraulic oil is reduced. The lock can be efficiently applied to the radial side surface, and the fixing and release of the stator 30 can be controlled in conjunction with the axial movement of the lock-up piston 20.
[0069]
As in the second embodiment, the contact surface 20a of the lock-up piston 20 is set with a wider surface to stabilize the transmission of force due to the movement of the lock-up piston 20 and reduce the load on the members. You may.
[0070]
Further, the friction member 33d provided on the support member 33 of the stator 30 may have a groove on the friction surface or a multi-plate structure, as in the first embodiment.
[0071]
【The invention's effect】
As described above, according to the present invention, the engagement and disengagement of the stator can be more reliably controlled with a simple structure while omitting the conventional complicated one-way clutch.
[Brief description of the drawings]
FIG. 1 is a sectional view showing an upper half of a torque converter with a lock-up clutch according to a first embodiment of the present invention.
FIG. 2 is a diagram showing a flow of hydraulic oil when a lock-up of a torque converter with a lock-up clutch according to the present invention is turned off.
FIG. 3 is a sectional view showing an upper half of a torque converter with a lock-up clutch according to a second embodiment of the present invention.
FIG. 4 is a sectional view showing an upper half of a torque converter with a lock-up clutch according to a third embodiment of the present invention.
[Explanation of symbols]
1 Torque converter
1A torque converter
1B torque converter
5 Transmission
12 Converter cover
13 Pump impeller
14 Turbine runner
15 Turbine hub
15a recess
15s Seal part
17 Lock-up clutch mechanism
18 Clutch member
19 Damper
20 Lock-up piston
20a per side
20s seal part
22 Clutch member
25 disc spring
26 Oil passage hole
30 Stator
33 Supporting member
33a first inner circumference
33b Second inner circumference
33c opposite side
33d friction member
35 bearing
37 bearing
40 Non-rotating member
40a counter surface
40L boss
41 Bypass channel
43a Seal part
43b Seal part
43s seal part
44 Connecting passage
45 opening
46 connecting passage
50 sleeve
52 channel
54 space
55 bush
60 Cover support member
100 input shaft
102 Oilway
SH space
SL pressure chamber

Claims (5)

A pump impeller connected to the engine output shaft via a cover member, a turbine runner disposed opposite to the pump impeller and connected to a transmission input shaft, and disposed between the pump impeller and the turbine runner. And a lock-up clutch including a ring-shaped piston that is disposed between the cover member and the turbine runner and that is movable in the axial direction.
An annular supporting member that supports the stator, and an annular non-rotating member that is provided to be non-rotatably opposed to the supporting member,
The support member and the non-rotating member are engaged in response to a first flow that generates a lock-up release pressure that separates the piston from the cover member, and causes the piston to contact the cover member. A torque converter device with a lock-up clutch, which is configured to be released in response to a second flow for generating a lock-up pressure to be generated. A flow path forming the first flow and the second flow;
A communication path introduced into a pressure chamber formed between the support member and the non-rotating member,
An opening for communicating the flow path and the communication path,
Further comprising
2. The torque converter device with a lock-up clutch according to claim 1, wherein the opening is provided downstream of the first flow near the support member and the non-rotating member. 3. The torque converter device with a lock-up clutch according to claim 2, wherein the flow passage near the opening is formed in a narrow path. Between the piston and the cover member, further comprising an elastic member that generates an urging force such that the piston is axially separated from the cover member,
The support member and the non-rotating member are engaged by promoting the urging force by the first flow, and are released against the urging force by the second flow. 2. The torque converter device with a lock-up clutch according to 1. The piston is liquid-tightly sealed and supported movably in the axial direction on an outer peripheral end face and an inner peripheral end face, and the support member and the non-rotating member are configured to support the first flow and the second flow. The torque converter device with a lock-up clutch according to claim 1, wherein the torque converter device is engaged / disengaged in conjunction with the axial movement of the piston due to a flow.

Images