JP2002021971A - Fluid coupling with baffle plate - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simultaneously satisfy the requirements of reducing the drag torque and improving the transmission efficiency in a fluid coupling with a baffle plate. SOLUTION: In this fluid coupling having the baffle plate 15 projected toward the inner periphery of a circulating circuit 5, a clutch chamber 17 communicating with the outer periphery side of the circulating circuit 5 is divided between the back of a turbine impeller 4 and a side cover 6 for covering the back of the impeller 4, a clutch piston 18 dividing the clutch chamber 17 into an inside chamber 17a of the turbine impeller 4 side and an outer chamber 17b on the side cover 6 side is connected to the turbine impeller 4 movably in the axial direction to constitute a lockup clutch L. A first oil passage 24 connected to the outer chamber 17b and a second oil passage 25 communicating with the inner periphery side of the circulating circuit are alternately switched to be communicated with the discharge side of the oil pump 27 and an oil reservoir 28.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a pump impeller connected to an input shaft and a turbine impeller connected to an output shaft arranged coaxially with the input shaft. The present invention relates to an improvement in a fluid coupling with a baffle plate, wherein a baffle plate is provided on at least one of both impellers and protruding toward the inner peripheral side of the circulation circuit.

[0002]

2. Description of the Related Art Such a fluid coupling with a baffle plate is disclosed in, for example, "Design of Fluid Power Transmission" according to Ohm Publishing.
As already disclosed on pages 24 and 25 of the US Pat.

[0003]

In such a fluid coupling with a baffle plate, the drag torque can be reduced by applying resistance to the flow of the working oil in the circulation circuit by the baffle plate. However, in the conventional one, the outside diameter of the baffle plate is set to be large in order to reduce the drag torque more sufficiently. However, in such a case, the flow of the working oil in the circulation circuit in the normal rotation range is reduced. There is an adverse effect that the transmission efficiency is greatly reduced because the transmission efficiency is greatly obstructed by the plate.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and has the above-mentioned fluid coupling with a baffle plate, which can simultaneously reduce drag torque and improve transmission efficiency without the above-mentioned adverse effects. The purpose is to provide. Another object is to improve the responsiveness of a mechanism used for improving the transmission efficiency.

[0005]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a pump impeller connected to an input shaft and a turbine impeller connected to an output shaft which are opposed to each other. In a fluid coupling with a baffle plate, an oil circulation circuit is formed, and at least one of the two impellers is provided with a baffle plate protruding toward the inner peripheral side of the circulation circuit. A clutch chamber communicating with the outer peripheral side of the circulation circuit is defined between a continuously provided side cover that covers the back of the turbine impeller, and the clutch chamber is defined as an inner chamber on the turbine impeller side and a side cover side. And a first oil passage connected to the outer chamber, the clutch piston being partitioned into an outer chamber of the first oil passage so as to be axially movably connected to the turbine impeller.
A first feature is that the second oil passage connected to the inner peripheral side of the circulation circuit is alternately connected to the discharge side of the oil pump and the oil reservoir. The input shaft and the output shaft correspond to a crankshaft 1 and a main shaft 2, respectively, in an embodiment of the present invention described later.

According to the first feature, when the input shaft is idling or rotating at an extremely low speed, the working oil discharged from the oil pump is supplied from the first oil passage to the outer chamber, the inner chamber, and the circulation circuit of the clutch chamber. By doing so, the lock-up clutch is disengaged and fluid transmission between the pump impeller and the turbine impeller is enabled. However,
At this time, the drag torque is reduced by the baffle plate obstructing the circulation of the working oil in the circulation circuit, and the stopped state of the output shaft can be easily maintained.

When the input shaft has reached a predetermined number of times after the start of fluid transmission, the operating oil discharged from the oil pump is supplied from the second oil passage to the circulation circuit and the inner chamber of the clutch chamber. By opening the outer chamber to the oil reservoir through the first oil passage, the lock-up clutch is connected, and the pump impeller and the turbine impeller are directly connected. As a result, the transmission efficiency between the input shaft and the output shaft can be increased irrespective of the decrease in the fluid transmission efficiency between the two impellers due to the baffle plate.

Therefore, it is possible to satisfy both the reduction of the drag torque and the improvement of the transmission efficiency between the two impellers during normal rotation.

Further, in addition to the first feature, the present invention provides a pump impeller hub surrounding a hub of a turbine impeller, and a bearing interposed between the hubs. A second feature is that two oil passages communicate with the inner peripheral side of the circulation circuit.

According to the second feature, the bearings can ensure the concentric accuracy of the pump impeller and the turbine impeller, and can ensure a smooth relative rotation between the two impellers. In addition, the working oil flowing into and out of the circulation circuit between the two impellers can be effectively lubricated by passing through the bearing. Not only that, but also the above-mentioned hydraulic oil is used for both the pump impeller and turbine impeller hubs,
In addition, since they flow along the baffle plate, they can be effectively cooled. Further, since the bearing also serves as a communication passage between the circulation circuit and the second oil passage, it can contribute to simplification of the oil passage configuration.

Further, in addition to the first or second feature, the present invention further comprises connecting the baffle plate to a hub of a turbine impeller, and connecting a second oil passage to an inlet of the pump impeller in the circulation circuit. This is a third feature.

According to the third feature, since the inlet of the pump impeller communicating with the second oil passage is at a relatively low pressure in the circulation circuit, the working oil is smoothly transferred from the second oil passage to the circulation circuit. , Which can contribute to improving the responsiveness of the lock-up clutch to the connected state.

Still further, according to the present invention, in addition to the first or second feature, the baffle plate is connected to a hub of a pump impeller, and a second oil passage communicates with an outlet of the turbine impeller in a circulation circuit. This is a fourth feature.

According to the fourth feature, since the outlet of the turbine impeller communicating with the second oil passage is at a relatively high pressure in the circulation circuit, when the lock-up clutch is not connected, the exit from the circulation circuit is established. The operation oil can smoothly flow out to the second oil passage, the responsiveness of the lock-up clutch to the disconnected state can be improved, and the fluid coupling can be effectively cooled. .

Further, in the present invention, in addition to the fourth feature, a fifth feature is that a second oil passage is also connected to the inlet of the pump impeller in the circulation circuit.

According to the fifth feature, when the lock-up clutch is not connected, the working oil can smoothly flow out of the circulation circuit to the second oil passage, and the cooling of the fluid coupling can be effectively performed. When the working oil is supplied from the second oil passage to the circulation circuit, the supply of the working oil can be performed smoothly, which can contribute to improving the responsiveness of the lock-up clutch to the connected state.

[0017]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on embodiments of the present invention shown in the accompanying drawings.

FIG. 1 is a longitudinal sectional view showing a fluid coupling with a baffle plate according to a first embodiment of the present invention in a state where a lock-up clutch is not connected, and FIG. FIG. 3 is a longitudinal sectional view showing a fluid coupling with a baffle plate according to a second embodiment of the present invention in a state where a lock-up clutch is not connected, and FIG. 4 is an operation showing a connection state of a lock-up clutch of the fluid coupling. FIG.

First, a first embodiment of the present invention shown in FIGS. 1 and 2 will be described.

A crankshaft 1 of an automobile engine and a main shaft 2 of a multi-stage transmission are coaxially arranged, and these are connected via a fluid coupling F.

The fluid coupling F includes a pump impeller 3 and a turbine impeller 4 opposed thereto and defining a working oil circulation circuit 5 therebetween. Each impeller 3, 4
Are the core rings 3 facing each other at the center of the circulation circuit 5.
c, 4c, and the inner peripheral wall of the core ring 4c of the turbine impeller 4 is arranged close to the inner peripheral wall of the core ring 3c of the pump impeller 3. By doing so, when the working oil flows through the circulation circuit 5 from the turbine impeller 4 to the pump impeller 3 side, it is possible to prevent the transmission efficiency from being lowered due to the penetration into the core rings 3c, 4c.

A side cover 6 for covering the back of the turbine impeller 4 is connected to the pump impeller 3. A flywheel 7 fixed to an end of the crankshaft 1 is connected to the side cover 6. You.

A hub 6a is provided at the center of the side cover 6.
The end of the main shaft 2 spline-connected to the hub 4b of the turbine impeller 4 is rotatably supported on the hub 6a via the bush 8.

The hub 3b of the pump impeller 3 is connected to the circulation circuit 5
Is arranged so as to surround the hub 4b of the turbine impeller 4 on the inner peripheral side, and a ball bearing 9 is interposed between the hubs 3b, 4b. At this time, the inner race 9a of the ball bearing 9 is fitted on the outer peripheral surface of the hub 4b and is axially sandwiched between the annular shoulder 10 of the hub 4b and the snap ring 11 locked on the hub 4b. . The outer race 9b of the ball bearing 9 is fitted on the inner peripheral surface of the hub 3b and is axially sandwiched between the annular shoulder 12 of the hub 3b and the retaining ring 13 locked on the hub 3b. Thus, both hubs 3b, 4b of the pump impeller 3 and the turbine impeller 4
Are axially connected via a ball bearing 9.
This ball bearing 9 is used for inner and outer races 9.
There is no seal through which the working oil can flow between a and 9b.

An annular baffle plate 15 projecting from the inner peripheral portion of the circulation circuit 5 toward the core ring 4c is integrally connected to the turbine impeller 4, and this baffle plate 1
An annular oil passage 16 is provided between the base of the pump 5 and the hub 3b of the pump impeller 3, and the inner peripheral end of the oil passage 16 communicates with the end face of the ball bearing 9 on the turbine impeller 4 side. Road 1
The outer peripheral end of 6 opens into the inlet of the pump impeller 3 in the circulation circuit 5.

Further, between the turbine impeller 4 and the side cover 6, a lock-up clutch L which can directly connect them is provided.
Is provided. The lock-up clutch L is defined between the rear surface of the turbine impeller 4 and the inner wall of the side cover 6, and has a clutch chamber 17 as an oil chamber communicating with the circulation circuit 5 and a clutch chamber 17. Inner chamber 17a on turbine impeller 4 side and outer chamber 17b on side cover 6 side
And a clutch piston 18 disposed in the clutch chamber 17 so as to be divided into two sections.
Is provided with a friction lining 18a on the end face facing the inner side wall of the side cover 6.

The clutch piston 18 is connected via a torque damper 20 to a plurality of transmission claws 21 projecting from the back of the turbine impeller 4, and has a friction lining 18a.
The outer peripheral surface of the hub 4b of the turbine impeller 4 is provided with a seal member 22 so as to be able to move in the axial direction between a connection position where the pressure is pressed against the inner wall of the side cover 6 and a non-connection position separated from the inner wall. Slidably supported.

The main shaft 2 is provided with a first oil passage 24 communicating with the outer chamber 17b of the lock-up clutch L. The hub 3b of the pump impeller 3 is integrally formed with a cylindrical oil pump drive shaft 26 that is arranged so as to surround the main shaft 2 and drives an oil pump 27. Second oil passage 2 communicating with the other end surface of ball bearing 9
5 is defined. Thus, the second oil passage 25 and the circulation circuit 5 communicate with each other via the ball bearing 9 and the annular oil passage 16.

The first oil passage 24 and the second oil passage 25 are connected by a switching valve 29 to the discharge side of the oil pump 27 and the oil reservoir 2.
8 are connected alternately.

Next, the operation of the first embodiment will be described.

When the engine is idling or operating at an extremely low speed, the switching valve 29 is connected to the first oil passage 2 as shown in FIG.
An electronic control unit (not shown) controls the connection of the second oil passage 4 to the discharge side of the oil pump 27 and the second oil passage 25 to the oil reservoir 28. Therefore, the rotational torque of the crankshaft 1 of the engine is
When the oil is transmitted to the side cover 6 and the pump impeller 3 and is driven to rotate, and the oil pump 27 is further driven, the discharge operating oil of the oil pump 27 is discharged from the switching valve 29 to the first valve.
Oil passage 24, outer chamber 17b and inner chamber 17 of clutch chamber 17
a, after flowing into the circulation circuit 5 and filling the circuit 5,
The oil passes through the annular oil passage 16 and the ball bearing 9 sequentially to the second oil passage 25, and is returned from the switching valve 29 to the oil reservoir 28.

In the clutch chamber 17, the outer chamber 17b is moved to the inner chamber 1 by the flow of the working oil as described above.
7a, and the pressure difference causes the clutch piston 18 to be pressed in a direction to be separated from the inner wall of the side cover 6, so that the lock-up clutch L is in the disconnected state, and the pump impeller 3 and the turbine impeller 4
Allows relative rotation between them. Therefore, when the pump impeller 3 is rotationally driven from the crankshaft 1, the circulation circuit 5
Circulates through the circulation circuit 5 as indicated by the arrow to transmit the rotational torque of the pump impeller 3 to the turbine impeller 4, but the baffle plate 15 intervening in the circulation circuit 5 circulates. By preventing the circulation of the working oil in the circuit 5, the drag torque is reduced, and the stopped state of the main shaft 2 can be easily maintained.

When the rotation speed of the crankshaft 1 is increased to start the vehicle, the rotation speed of the pump impeller 3 is increased at the same time, and the fluid transmission from the pump impeller 3 to the turbine impeller 4 becomes active. As a result, the turbine impeller 4 rotates to drive the main shaft 2, and a smooth start is possible.

After the engine starts, when the engine speed exceeds a predetermined value, the switching valve 2 by the electronic control unit (not shown).
As shown in FIG. 2, the second oil passage 25 is connected to the discharge side of the oil pump 27, and the first oil passage 24 is connected to the oil reservoir 28 by the switching of 9. As a result, the operating oil discharged from the oil pump 27 passes through the second oil passage 25 from the switching valve 29, and the ball bearing 9
After flowing into the circulation circuit 5 through the annular oil passage 16 in order, and filling the circuit 5, it moves to the inner chamber 17a of the clutch chamber 17 and also fills the chamber 17a. On the other hand, the outer chamber 17b of the clutch chamber 17 is opened to the oil reservoir 28 via the first oil passage 24 and the switching valve 29.
The pressure in the inner chamber 17a becomes higher than that in the outer chamber 17b, and the pressure difference causes the clutch piston 18 to be pressed against the side cover 6 so that the friction lining 18a is pressed against the inner wall of the side cover 6, and the lock-up clutch L The connection state is established.

According to such connection of the lock-up clutch L, since the pump impeller 3 and the turbine impeller 4 are directly connected to each other, the rotation of the crankshaft 1 can be performed irrespective of the decrease in the fluid transmission efficiency due to the baffle plate 15. Torque can be transmitted to the main shaft 2 efficiently, that is, high transmission efficiency can be attained, and fuel consumption can be reduced.

Thus, it is possible to satisfy both the reduction of the drag torque and the improvement of the transmission efficiency between the impellers 3 and 4 during the normal operation of the engine.

Since hydraulic oil flows between the circulation circuit 5 and the second oil passage 25 via the ball bearing 9 and the annular oil passage 16, the fluid coupling F is cooled and the bearing 9 is lubricated. Can be effectively promoted. In particular, since the annular oil passage 16 is opened in the circulation circuit 5 at the entrance of the pump impeller 3 of a relatively low pressure, the annular oil passage 16 passes from the second oil passage through the ball bearing 9 and the annular oil passage 16 as shown in FIG. The working oil can be smoothly supplied to the circulation circuit 5, and the responsiveness of the lock-up clutch L to the connected state can be improved.

The ball bearing 9 and the annular oil passage 16
The working oil passing through the pump impeller 3 and the turbine impeller 4 flows along both the hubs 3b and 4b and the baffle plate 15, so that they can be effectively cooled.

Further, since the ball bearing 9 also serves as a communication path between the circulation circuit and the second oil path, the configuration of the oil path is simplified, so that the number of processing steps and the cost can be reduced.

Further, a ball bearing 9 is interposed between the hub 4b of the turbine impeller 4 and the hub 3b of the pump impeller 3 surrounding the hub, and both impellers 3, 4 are interposed via the ball bearing 9. The hubs of the pump impeller 3, the turbine impeller 4, and the side cover 6 are provided with high concentric accuracy because the hubs are connected in the axial direction, thereby constituting a fluid coupling assembly. be able to. Therefore, the hub 4b of the turbine impeller 4 and the side cover 6,
The work of fitting the main shaft 2 to the shaft 6a can be easily performed.
Moreover, since the hub 3b of the pump impeller 3 is supported by the hub 4b of the turbine impeller 4 via the ball bearing 9, it is not necessary to fit the main shaft 2 to the hub 3b of the pump impeller 3. Thus, the workability of attaching the main shaft 2 can be remarkably improved.

Further, since the pump impeller 3 and the turbine impeller 4 are provided with high concentric accuracy by the ball bearing 9, smooth relative rotation is ensured and a stable coupling function can be exhibited.

Next, a second embodiment of the present invention shown in FIGS. 3 and 4 will be described.

In the second embodiment, the baffle plate 1
5 is integrally connected to the hub 3b of the pump impeller 3, and between the hub 3b and the hub 4b of the turbine impeller 4,
An annular oil passage 30 is provided in the circulation circuit 5 at an outlet of the turbine impeller 4. The annular oil passage 30 communicates with the second oil passage 25 via the ball bearing 9.

The hub 3b of the pump impeller 3 has a second
A plurality of radial oil passages 31 communicating the oil passage 25 with the inlet of the pump impeller 3 in the circulation circuit 5 are provided.

When the lock-up clutch L shown in FIG. 3 is not connected, the working oil flowing from the first oil passage 24 into the outer chamber 17b, the inner chamber 17a of the clutch chamber 17 and the circulation circuit 5 is supplied to the turbine impeller 4 , And flows out from the inlet of the pump impeller 3 to the radial oil passage 31 to the second oil passage 25.

In particular, since the outlet of the turbine impeller 4 where the annular oil passage 30 opens is at a relatively high pressure in the circulation circuit 5, the outflow of working oil from the circulation circuit 5 to the annular oil passage 30 is promoted. Thus, the responsiveness of the lock-up clutch L to the disconnected state can be improved, and the fluid coupling F can be effectively cooled. In addition, the working oil passes through the ball bearing 9 to the second oil passage 25, so that the bearing 9 can be effectively lubricated.

Since the inlet of the pump impeller 3 where the radial oil passage 31 is open is located at a relatively low pressure in the circulation circuit 5, as shown in FIG.
When the working oil is supplied to the circulation circuit 5 through the control unit 1, the supply can be performed smoothly, and the responsiveness of the lock-up clutch L to the connected state can be improved.

Since other structures are the same as those of the previous embodiment, the same reference numerals are given to the portions corresponding to those of the previous embodiment in FIGS. 3 and 4, and the description thereof will be omitted.

The present invention is not limited to the above-described embodiment, and various design changes can be made without departing from the gist of the present invention. For example, in the first embodiment of FIG. 1, the baffle plate 15 can be formed separately from the hub 4b of the turbine impeller 4, and connected to the hub 4b by welding or the like, and the second embodiment of FIG. In the example, the baffle plate 15
Can be formed separately from the hub 3b of the pump impeller 3 and connected to the hub 3b by welding or the like. Also, instead of the ball bearing 9, another type of bearing that allows the flow of the working oil can be used.

[0050]

As described above, according to the present invention, in a fluid coupling with a baffle plate, between a back surface of a turbine impeller and a side cover connected to the pump impeller and covering the back surface of the turbine impeller. A clutch chamber communicating with the outer peripheral side of the circulation circuit is defined, and a clutch piston which partitions the clutch chamber into an inner chamber on the turbine impeller side and an outer chamber on the side cover side is axially moved to the turbine impeller. A first oil passage connected to the outer chamber and a second oil passage connected to the inner peripheral side of the circulation circuit are alternately connected to the discharge side of the oil pump and the oil reservoir. Since the communication is switched, the communication between the first and second oil passages, the oil pump and the oil reservoir is switched,
It is possible to satisfy both the reduction of the drag torque and the improvement of the transmission efficiency between the two impellers during normal rotation.

Further, according to the present invention, the hub of the pump impeller is arranged so as to surround the hub of the turbine impeller, and the second oil passage is circulated through the bearing interposed between the hubs. By communicating with the inner peripheral side of the circuit, the bearings can ensure the concentric accuracy of the pump impeller and the turbine impeller, and can ensure smooth relative rotation of both impellers. Moreover, the working oil flowing into and out of the circulation circuit between the two impellers can be effectively lubricated by passing through the bearings. In addition, the working oil can be effectively lubricated by both the pump impeller and the turbine impeller. In addition, by flowing along the baffle plate, they can be effectively cooled. Further, since the bearing also serves as a communication passage between the circulation circuit and the second oil passage, it can contribute to simplification of the oil passage configuration.

Further, according to the present invention, the baffle plate is connected to the hub of the turbine impeller, and the second oil passage communicates with the inlet of the pump impeller in the circulation circuit, thereby circulating from the second oil passage. The operating oil can be smoothly supplied to the circuit, which can contribute to improving the response to the connected state of the lock-up clutch.

Still further, according to the present invention, the baffle plate is connected to the hub of the pump impeller, and the second oil passage communicates with the outlet of the turbine impeller in the circulation circuit, so that the lock-up clutch is disconnected. In this state, the hydraulic oil can smoothly flow out of the circulation circuit to the second oil passage, improving the responsiveness of the lock-up clutch to the disconnected state, and effectively cooling the fluid coupling. Can be done

According to the present invention, furthermore, in the circulation circuit,
By connecting the second oil passage to the inlet of the pump impeller, when the lock-up clutch is not connected, the working oil can smoothly flow from the circulation circuit to the second oil passage, and the fluid coupling Cooling can be performed effectively, and when the operating oil is supplied from the second oil passage to the circulation circuit, it can be smoothly supplied and the responsiveness to the connected state of the lock-up clutch is improved. Can contribute.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a fluid coupling with a baffle plate according to a first embodiment of the present invention in a state where a lock-up clutch is not connected.

FIG. 2 is an operation explanatory view showing a connected state of a lock-up clutch of the fluid coupling.

FIG. 3 is a longitudinal sectional view showing a fluid coupling with a baffle plate according to a second embodiment of the present invention in a state where a lock-up clutch is not connected.

FIG. 4 is an operation explanatory view showing a connected state of a lock-up clutch of the fluid coupling.

[Explanation of symbols]

 F ····· Fluid coupling L · ····· Lock-up clutch 1 ······ Input shaft (crank shaft of engine) 2 ······ Output shaft (main shaft of transmission) 3 ···· · Pump impeller 3b ··· Pump hub impeller 4 ··· Turbine impeller 4b ··· Turbine impeller hub 5 ···· Circulation circuit 6 ····· Side cover 9 ······ Bearing (ball bearing) 15 ··· Baffle plate 17 ··· Clutch chamber 17a ··· Inner chamber 17b ··· Outer chamber 18 ··· Clutch piston 24 ··· First Oil passage 25 ... second oil passage 27 ... oil pump 28 ... oil reservoir 29 ... switching valve

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Atsaku Suzuki 508-1 Toyocho, Hamamatsu-shi, Shizuoka Pref. Yutaka Giken Co., Ltd. (72) Inventor Yoshihisa Sugimura 508-1 Toyocho, Hamamatsu-shi, Shizuoka Pref. Inside the Giken (72) Inventor Hidetaka Koga 8 Dosana, Fujisawa-shi, Kanagawa Prefecture Isuzu Motors Fujisawa Plant Co., Ltd. (72) Inventor Nobuyuki Iwao 8 Dosana, Fujisawa-shi, Kanagawa Prefecture Isuzu Central Research Institute Co., Ltd. (72) Invention Person Yasushi Yamamoto 8 Tsuchiya, Fujisawa City, Kanagawa Prefecture Isuzu Central Research Institute Co., Ltd.

Claims (5)

[Claims] An impeller (3) connected to an input shaft (1) and a turbine impeller (4) connected to an output shaft (2) are opposed to each other, and a hydraulic oil circulation circuit is interposed therebetween. In a fluid coupling with a baffle plate, a baffle plate (15) projecting toward the inner peripheral side of the circulation circuit (5) is attached to at least one of the two impellers (3, 4). Between the back of the impeller (4) and a side cover (6) connected to the pump impeller (3) and covering the back of the turbine impeller (4), on the outer peripheral side of the circulation circuit (5). A communicating clutch chamber (17) is defined, and this clutch chamber (17) is partitioned into an inner chamber (17a) on the turbine impeller (4) side and an outer chamber (17b) on the side cover (6) side. Axial clutch piston (18) to turbine impeller (4) The outer chamber (17b) is movably connected to form a lock-up clutch (L).
A first oil passage (24) connected to the oil pump (2) and a second oil passage (25) connected to the inner peripheral side of the circulation circuit (5) are connected to an oil pump (2).
7) A fluid coupling with a baffle plate, wherein the communication is alternately switched between the discharge side and the oil reservoir (28). 2. A fluid coupling with a baffle plate according to claim 1, wherein the hub (4b) of the turbine impeller (4).
The hub (3b) of the pump impeller (3) is arranged so as to surround the second oil passage (25) through the bearing (9) interposed between the hubs (3b, 4b). A fluid coupling with a baffle plate, wherein the fluid coupling communicates with an inner peripheral side of the circulation circuit (5). 3. The fluid coupling with a baffle plate according to claim 1, wherein said baffle plate (15).
Characterized in that a baffle is connected to a hub (4b) of a turbine impeller (4), and a second oil passage (25) communicates with an inlet of a pump impeller (3) in the circulation circuit (5). Fluid coupling with plate. 4. The fluid coupling with a baffle plate according to claim 1, wherein said baffle plate (15).
Characterized in that a baffle is connected to a hub (3b) of a pump impeller (3), and a second oil passage (25) is connected to an outlet of a turbine impeller (4) in the circulation circuit (5). Fluid coupling with plate. 5. The fluid coupling with a baffle plate according to claim 4, wherein a second oil passage (25) is also connected to an inlet of a pump impeller (3) in the circulation circuit (5). Fluid coupling with baffle plate.