JP2003156122A - Fluid coupling - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid coupling which effectively reduces drag torque without deteriorating transmission torque at high speed rotation. SOLUTION: The fluid coupling is provided with a pump having a pump shell having an annular coring, and a turbine arranged facing the pump and having a turbine shell having an annular coring. A baffle mechanism is arranged in a fluid circulation passage formed by the pump shell and the turbine shell. The baffle mechanism is provided with a flap turnably supported on an inner circumferential part of the coring of the pump shell or turbine shell, and a spring member positioning a one side rim of the flap in a center part of the fluid circulation passage in a slow state of a rotational speed of the pump or turbine in correspondence to centrifugal force acting on the flap and positioning the one side rim of the flap in an inner circumferential part side of the coring of the turbine shell or pump shell in a fast state of the rotational speed of the pump or turbine.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid coupling (fluid coupling) for transmitting rotational torque of a prime mover.
Regarding the improvement of.

[0002]

2. Description of the Related Art Fluid couplings have been conventionally used as power transmission couplings for ships, industrial machines and automobiles. The fluid coupling includes a pump having an annular pump shell and a plurality of impellers radially arranged in the pump shell, an annular pump shell and a plurality of impellers radially arranged in the pump shell. And a turbine arranged to face the pump, and the working fluid is filled in the pump and the turbine. In the fluid coupling thus configured, the pump is connected to, for example, a crankshaft (input shaft as a fluid coupling) of a diesel engine, which is a prime mover, and the turbine is attached to an output shaft arranged on the same axis as the input shaft. .. Further, a fluid coupling in which an annular core ring for rectifying the working fluid is provided in the pump shell and the turbine shell is also used.

FIG. 11 shows the characteristics of a general fluid coupling. The horizontal axis represents the speed ratio (e) between the pump and the turbine, and the vertical axis represents the input capacity coefficient (τ) of the fluid coupling. As can be seen from FIG. 11, the fluid coupling has the maximum input capacity coefficient (τ) when the speed ratio (e) between the pump and the turbine is zero (0), that is, when the pump is rotating and the turbine is stopped. When a vehicle drive device is equipped with a fluid coupling having such characteristics, the engine is driven and the transmission gears are turned on when the vehicle is stopped, that is, the input shaft rotates and the output shaft stops. In the state in which it is in the open state, it has a drag torque due to its characteristics. Drag torque is generally the engine's idling speed (eg 500 rpm)
It means the transmission torque in the state of being operated. This drag torque has a rotational speed ratio (e) of the pump and the turbine that maximizes the design point of the fluid coupling from 0.95 to 0.9.
In 8th place, it gets quite large. If the drag torque is large, the idling operation of the engine becomes extremely unstable, and this unstable rotation causes abnormal vibration in the drive system. In addition, the large drag torque also causes deterioration of fuel efficiency during idling.

As a measure for reducing the drag torque described above, there is known a technique of disposing a baffle plate between a pump and a turbine. A drag torque reduction measure provided with a baffle plate will be described with reference to FIGS. 12 and 13. In the fluid coupling shown in FIGS. 12A and 12B, an annular baffle plate BP attached to the output shaft OS is arranged between the pump P and the turbine T. The fluid coupling shown in FIG.
An annular baffle plate BP is arranged on the outer peripheral portion of the pump P.

In the fluid coupling shown in FIGS. 12 (a) and 12 (b), at low speed rotation, the working fluid, to which the rotational force is given by the rotation of the pump P as shown in FIG. The working fluid that has driven the turbine T has its centrifugal force attenuated and flows into the pump P toward the coring side. Therefore, at the time of low speed rotation, the effect of the baffle plate BP arranged between the pump and the turbine is small, and the drag torque described above cannot be reduced. Further, at the time of high speed rotation, the working fluid to which the rotational force is given by the rotation of the pump P shown in FIG. 12B flows into the turbine T from the outer peripheral side by the centrifugal force, but the working fluid flowing into the turbine T is the centrifugal force. Since it is strong, it flows along the inner surface of the turbine shell, so when it flows into the pump P, the baffle plate BP
Abut. Therefore, at the time of high speed rotation, the baffle plate BP acts largely and the transmission torque (coupling efficiency) is lowered. As described above, the fluid couplings shown in FIGS. 12A and 12B cannot reduce the drag torque that is desired to be reduced during low-speed rotation such as during idling of the engine, and also transfer torque (coupling efficiency) during high-speed rotation. ) Will be a less efficient joint.

Further, the fluid coupling shown in FIG.
Since the annular baffle plate BP is disposed on the outer peripheral portion of the, the drag torque at the time of low speed rotation can be reduced, but the transmitted torque is significantly reduced at the time of high speed rotation. That is, the working fluid, which is given a rotational force by the rotation of the pump P, flows to the outer peripheral side by the centrifugal force, but when the flow velocity is maximized and flows out from the pump P, the working fluid collides with the baffle plate BP and the flow velocity is attenuated. Since it flows into the turbine T, there is a problem that the transmission torque (coupling efficiency) is significantly reduced during high speed rotation.

In order to solve the above-mentioned problems, the applicant of the present invention has found that in a fluid coupling including a pump shell having an annular core ring and a turbine shell having an annular core ring, one core ring has an inner circumference or an outer circumference. A fluid coupling in which an annular baffle plate is attached to
Proposed as 1-50309.

[0008]

DISCLOSURE OF THE INVENTION Problems to be Solved by the Invention
Even in the fluid coupling proposed as −50309, since the baffle plate always protrudes in the body circulation path by the predetermined amount, the drag torque can be effectively reduced, but the transmission torque at the time of high speed rotation does not decrease. Inevitable. .

The present invention has been made in view of the above facts, and its main technical problem is to provide a fluid coupling capable of effectively reducing drag torque without reducing transmission torque during high-speed rotation. To do.

[0010]

According to the present invention, in order to solve the above-mentioned main technical problems, an annular pump shell having an annular core ring and a plurality of annular pump shells arranged in the pump shell are provided. A turbine having an impeller, an annular turbine shell facing the pump and having an annular core ring, and a turbine having a plurality of runners disposed in the turbine shell. In the fluid coupling, a flap that is disposed in a fluid circulation path formed by the pump shell and the turbine shell and has one side edge rotatably supported by an inner peripheral portion of a core ring of the pump shell, and the flap. Corresponding to the centrifugal force acting on the pump, the other side edge of the flap is positioned at the center of the fluid circulation path when the rotation speed of the pump is slow, and the flap is fast when the rotation speed of the pump is fast. The other side edge of the-up is provided with a baffle mechanism having a regulating means for positioning the inner peripheral portion side of the core ring of the turbine shell, the fluid coupling is provided, characterized in that.

It is desirable that a plurality of the flaps be arranged along the core ring of the pump shell, and that a weight member be attached to the other end edges of the several baffle plates. desirable. The restricting means comprises a spring member arranged between the plurality of baffle plates and the pump shell.

Further, according to the present invention, a pump having an annular pump shell having an annular core ring, and a plurality of impellers arranged in the pump shell, and arranged to face the pump. And a turbine having an annular turbine shell having an annular core ring and a plurality of runners disposed in the turbine shell, the fluid coupling being formed by the pump shell and the turbine shell. A flap disposed in the fluid circulation path and having one side edge rotatably supported on the inner peripheral portion of the core ring of the turbine shell, and a centrifugal force acting on the flap,
When the rotational speed of the pump is low, the other side edge of the flap is positioned at the center of the fluid circulation path, and when the rotational speed of the turbine is high, the other side edge of the flap is inside the core ring of the pump shell. A fluid coupling is provided, which is provided with a baffle mechanism having a regulating means positioned on the peripheral side.

It is desirable that a plurality of the flaps be arranged along the core ring of the turbine shell,
Further, it is desirable that a weight member is attached to the other end edge portions of the above-mentioned several baffle plates. The above regulation means
The spring member is disposed between the plurality of baffle plates and the turbine shell.

Further, according to the present invention, a pump having an annular pump shell, a plurality of impellers arranged in the pump shell, and an annular turbine shell arranged so as to face the pump. And a turbine having a plurality of runners disposed in the turbine shell, the fluid coupling being provided in the fluid circulation path formed by the pump shell and the turbine shell, and having one side edge. And a flap rotatably supported on the inner peripheral portion of the pump shell and attached to the flap respectively, and actuate the other side edges of the plurality of flaps to the inner peripheral side of the turbine shell by the action of centrifugal force. Corresponding to the weight member to be biased and the centrifugal force acting on the weight member, the other side edge of the flap is positioned at the center of the fluid circulation path when the rotation speed of the pump is slow, and the rotation speed of the pump is In There state is provided with a baffle mechanism having a regulating means for positioning the other side edge of the flap to the inner peripheral portion of the turbine shell, the fluid coupling is provided, characterized in that.

It is desirable that a plurality of flaps be arranged along the pump shell. The restricting means is composed of a spring member arranged between the plurality of flaps and the pump shell.

Further, according to the present invention, a pump having an annular pump shell, a plurality of impellers arranged in the pump shell, and an annular turbine shell arranged to face the pump. And a turbine having a plurality of runners disposed in the turbine shell, the fluid coupling being provided in the fluid circulation path formed by the pump shell and the turbine shell, and having one side edge. And a flap rotatably supported on the inner peripheral portion of the turbine shell and attached to the flap, respectively, and actuating the other side edges of the plurality of flaps to the inner peripheral side of the pump by the action of centrifugal force. Corresponding to the weight member and the centrifugal force acting on the weight member, when the rotation speed of the pump is slow, the other side edge of the flap is positioned at the center of the fluid circulation path so that the rotation speed of the pump is high. In the fluid coupling, characterized in that, the other side edge of the flap is provided with a baffle mechanism having a regulating means for positioning the inner periphery of the pump shell is provided.

It is desirable that a plurality of flaps be arranged along the turbine shell. The restriction means is composed of a spring member arranged between the plurality of flaps and the turbine shell.

[0018]

BRIEF DESCRIPTION OF THE DRAWINGS In the following, a more detailed description will be given with reference to the accompanying drawings, which illustrate preferred embodiments of a fluid coupling constructed according to the present invention.

FIG. 1 shows an embodiment of a drive device in which a fluid coupling constructed according to the present invention is arranged between an automobile engine and a friction clutch. The drive system in the illustrated embodiment includes an internal combustion engine 2 as a prime mover, a fluid coupling 4 and a friction clutch 6 configured according to the present invention. The internal combustion engine 2 is a diesel engine in the illustrated embodiment, and a pump side of the fluid coupling 4 described later is attached to an end portion of the crankshaft 21.

The fluid coupling 4 is arranged in a fluid coupling housing 40 which is attached to the housing 22 mounted on the diesel engine 2 by fastening means such as bolts 23. The fluid coupling 4 in the illustrated embodiment includes a pump 41 and a turbine 4 arranged to face the pump 41.
2 and a casing 43 connected to the pump 41.

The pump 41 constituting the fluid coupling 4 is a bowl-shaped pump shell 412 having an annular core ring 411.
And a plurality of impellers 413 radially arranged in the pump shell 412.
2 is attached to the casing 43 by fixing means such as welding. The casing 43 has a bolt 441 and a nut 4 on the outer peripheral portion of a drive plate 44, the inner peripheral portion of which is attached to the crankshaft 21 by the bolt 24.
It is attached by fastening means such as 42. In this way, the pump shell 412 of the pump 41 is connected to the crankshaft 2 via the casing 43 and the drive plate 44.
Connected to 1. Therefore, the crankshaft 21 is connected to the fluid coupling 4
Function as the input axis of. A ring gear 45 for starting that meshes with a drive gear of a starter motor (not shown) is mounted on the outer periphery of the drive plate 44.

The turbine 42 is a bowl-shaped turbine shell 422 provided to face the pump shell 412 of the pump 41 and provided with an annular core ring 421, and radially arranged in the turbine shell 422. And a plurality of runners 423. The turbine shell 421 is attached to a turbine hub 47, which is spline-fitted to an output shaft 46 arranged on the same axis as the crankshaft 21 as the input shaft, by fixing means such as welding.

The fluid coupling 4 in the embodiment of FIG. 1 is arranged in the fluid circulation passage 400 formed by the pump shell 412 and the turbine shell 422, and the amount of advance into the fluid circulation passage 400 when the rotation speed is low. Is large and the rotation speed is high, the baffle mechanism 5 for reducing the amount of advance into the fluid circulation path 400 is provided. The baffle mechanism 5 will be described in detail later.

Continuing with reference to FIG. 1, the fluid coupling 4 in the illustrated embodiment comprises a hydraulic pump 60. The hydraulic pump 60 is arranged in a pump housing 62 which is attached to a clutch housing 70, which will be described later, of the friction clutch 7 mounted in the fluid coupling housing 40 by a fixing means such as a bolt 61. The hydraulic pump 60 is the pump shell 41 of the pump 41.
It is configured to be rotationally driven by a pump hub 48 attached to the pump 2, and supplies a working fluid into the pump 41 and the turbine 42 via a fluid path (not shown). The pump hub 48 is rotatably supported on the turbine hub by bearings 49.

Next, the friction clutch 7 will be described. The friction clutch 7 includes a clutch housing 70 mounted on the fluid coupling housing 40 with bolts 71.
It is arranged inside. The friction clutch 7 in the illustrated embodiment includes a clutch drive plate 72 mounted on the output shaft 46 of the fluid coupling 4 and a transmission shaft 73 (in the illustrated embodiment, disposed on the same axis as the output shaft 46). , An input shaft of a transmission (not shown), a driven plate 76 mounted on a clutch hub 74 spline-fitted to the transmission shaft 73 and having a clutch facing 75 mounted on the outer periphery thereof, and the driven plate 76 is a clutch drive. A pressure plate 77 that presses against the plate 72, a diaphragm spring 78 that urges the pressure plate 77 toward the clutch drive plate 72, and an intermediate portion of the diaphragm spring 78 that engages with the inner end portion of the diaphragm spring 78. Fulcrum 7
A release bearing 79 that operates as 81 and a clutch release fork 80 that axially operates the release bearing 79 are provided. In the friction clutch 7 configured as described above, the pressure plate 77 is pressed toward the clutch drive plate 72 by the spring force of the diaphragm spring 78 in the state shown in the drawing, and therefore, the clutch facing mounted on the driven plate 76 is pressed. The power transmitted from the clutch drive plate 72 to the output shaft 46 of the fluid coupling 4 by the clutch drive plate 72 is transmitted to the transmission shaft 73 via the clutch drive plate 72 and the driven plate 76. To cut off this power transmission, hydraulic pressure is supplied to a slave cylinder (not shown) to operate the clutch release fork 80, and the release bearing 79 is moved to the left in FIG.
It is operated as shown by the dotted line, and the pressing force on the pressure plate 77 is released, so that the power transmission from the clutch drive plate 72 to the driven plate 76 is cut off.

The drive unit equipped with the fluid coupling in the illustrated embodiment is configured as described above, and its operation will be described below. The driving force generated on the crankshaft 21 (input shaft) of the diesel engine 2 is transmitted to the casing 43 of the fluid coupling 4 via the drive plate 44. Pump shell 412 of casing 43 and pump 41
Are integrally formed, the pump 41 is rotated by the driving force. When the pump 41 rotates, the working fluid in the pump 41 is centrifugally exerted by the impeller 413.
Along the direction toward the outer circumference, and flows into the turbine 42 side as indicated by the arrow. The working fluid that has flowed into the turbine 42 side flows toward the inner peripheral side, as shown by the arrows, in the pump 4
Set back to 1. In this way, the working fluid in the pump 41 and the turbine 42 circulates in the pump 41 and the turbine 42, whereby the driving torque on the pump 41 side is transmitted to the turbine 42 side via the working fluid. The driving force transmitted to the turbine 42 side is transmitted to the output shaft 46 via the turbine shell 421 and the turbine hub 47, and is further transmitted to the transmission (not shown) via the friction clutch 6.

Next, a first embodiment of the baffle mechanism 5 will be described with reference to FIGS. 2 and 3. First
The baffle mechanism 5 in the embodiment of
Core ring 411 of the pump shell 412 within the fluid circuit 400 formed by the turbine shell 12 and the turbine shell 422.
A plurality of (six in the illustrated embodiment) flaps 51 are provided along the inner circumference of the flap. One side edge of the plurality of flaps 51 is rotatably supported on the inner peripheral portion of the core ring 411 of the pump shell 412. Specifically, the flap support member 52 is attached to the inner peripheral portion of the core ring 411 of the pump shell 412 by welding, and one side edge of the flap 51 is connected to a position corresponding to both sides of the flap support member 52. 511 and 511 are provided. The flap 51 is rotatably supported by the core ring 411 of the pump shell 412 by inserting the connecting portions 511, 511 and the flap support member 52 and disposing the support pin 53. In addition, flap 5
1 is formed of, for example, an aluminum alloy,
A weight member 54 made of a metal having a high specific gravity such as copper or lead is joined to the other side edge portion by brazing.

The baffle mechanism 5 in the first embodiment
Corresponds to the centrifugal force acting on the plurality of flaps 51, and when the rotation speed of the pump 41 is low, the other side edge of the plurality of flaps 51 is positioned at the center of the fluid circulation path 400 to rotate the pump 41. When the speed is high, a regulation means 55 is provided for positioning the other side edges of the plurality of flaps 51 on the inner peripheral side of the core ring 421 of the turbine shell 422. In the illustrated embodiment, the restricting means 55 includes the weight member 54 mounted on the flap 51 and the pump shell 4
Tension coil spring 5 arranged between the inner circumference of 12 and
It is composed of a spring member such as 51. The tension coil spring 551 is set so that the other side edge of the flap 51 is positioned at the center of the fluid circulation path 400 as shown in the upper half of FIGS. 2 and 3 until the rotational speed of the pump 41 reaches a predetermined value. The load is set. When the rotation speed of the pump 41 becomes faster than a predetermined value, the flap 51
Since the centrifugal force acting on the weight member 54 and the weight member 54 increases, as shown in the lower half of FIGS.
Rotates the other side edge so as to be positioned on the inner peripheral side of the core ring 421 of the turbine shell 422 around the support pin 53 against the spring force of the tension coil spring 551.

As described above, according to the baffle mechanism 5 in the first embodiment, the pump 41 is rotated until it reaches a predetermined value (for example, 500 rpm which is the idling speed of the diesel engine), as shown in FIGS. In the upper half of the drawing, the spring force of the tension coil spring 551 causes the other side edge of the flap 51 to move to the fluid circulation path 40.
It is located in the center of 0. Therefore, while the engine is idling, the working fluid, which is given a rotational force by the rotation of the pump 41, circulates through the turbine 42 as shown by the arrow in FIG.
Since the flap 51 is positioned so as to greatly advance in 00, the working fluid collides with the flap 51 and the flow velocity is attenuated, so that the transmission torque is reduced. Therefore, the drag torque during the idling operation of the engine in which the speed ratio (e) between the pump and the turbine is zero (0), that is, the pump is rotating and the turbine is stopped can be reduced. On the other hand, when the rotation speed of the pump 41 becomes higher than a predetermined value, the centrifugal force acting on the flap 51 and the weight member 511 increases, so that the other end edge of the flap 51 has a lower edge as shown in the lower half of FIGS. 2 and 3. It is rotated to the turbine shell 422 side around the support pin 53 against the spring force of the tension coil spring 551, and is positioned on the inner peripheral side of the core ring 421. As a result, the amount of projection of the flap 51 into the fluid circulation path 400 becomes small, and the working fluid that circulates flows into the pump 41 without being substantially affected by the action of the flap 51. Therefore, the transmission efficiency is high during high-speed engine operation. Does not cause a decrease in

As described above, in the baffle mechanism 5 according to the first embodiment, the flap 51 operates according to the rotation speed of the pump 41. Therefore, the fluid coupling equipped with the baffle mechanism 5 in the first embodiment has the characteristics shown in FIG. 10 corresponding to the rotation speed of the pump 41, that is, the engine. In FIG. 10, the horizontal axis represents the speed ratio (e) between the pump and the turbine, and the vertical axis represents the input capacity coefficient (τ) of the fluid coupling. In FIG. 10, the broken line shows the characteristics of the diesel engine at idling speed (for example, 500 rpm), and the dashed line shows the engine speed at start (for example, 1).
000 rpm), the solid line is the characteristic at the maximum engine torque (for example, 1500 rpm). That is, since the fluid coupling equipped with the baffle mechanism 5 according to the first embodiment can obtain the characteristic corresponding to the engine operating state, it is possible to reduce the drag torque at the time of idling and to improve the driving feeling of the driver. A matched transmission torque can be obtained and the vehicle can be started smoothly.

Next, the baffle mechanism 5a according to the second embodiment will be described with reference to FIGS. 4 and 5.
The baffle mechanism 5a in the second embodiment is one in which the constituent members of the baffle mechanism 5 in the first embodiment are arranged on the turbine 42 side. Therefore, in the baffle mechanism 5a in the second embodiment, the same members as those of the baffle mechanism 5 in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted. The baffle mechanism 5a in the second embodiment is the pump shell 4
12 and the turbine shell 422 are arranged in a fluid circulation path 400, and one side edge of the turbine shell 4 is provided.
A plurality of (six in the illustrated embodiment) flaps 51 rotatably supported by 22 core rings 421;
When the rotation speed of the turbine 42 is slow corresponding to the centrifugal force acting on the plurality of flaps 51, the other side edge of the plurality of flaps 551 is positioned at the center of the fluid circulation path 400, and the rotation speed of the turbine 42 is In a fast state, there are provided regulation means 53 for positioning the other side edges of the plurality of flaps 51 to the inner peripheral side of the core ring 411 of the pump shell 412. The baffle mechanism 5a in the second embodiment is
In the core ring 421 of the turbine shell 422.
A flap support member 52 is attached to the inner peripheral portion of the by welding, and connecting portions 511 and 511 are provided at positions corresponding to both sides of the flap support member 52 at one side edge of the flap 51. The flap 51 is rotatably supported by the core ring 411 of the pump shell 412 by inserting the connecting portions 511, 511 and the flap support member 52 and disposing the support pin 53. Further, in the baffle mechanism 5a according to the second embodiment, the tension coil spring 551 as the restricting means 55 has the flap 51.
It is arranged between the weight member 54 mounted on the inner wall of the turbine shell 422 and the inner peripheral portion of the turbine shell 422.

Baffle mechanism 5a in the second embodiment
Is configured as described above, pulling the turbine 42 as shown in the upper half of FIGS. 4 and 5 until the rotational speed of the turbine 42 reaches a predetermined value (for example, 500 rpm which is the idling rotational speed of a diesel engine). The other side edge of the flap 51 is positioned at the center of the fluid circulation path 400 by the spring force of the coil spring 531. Therefore, the drag torque during the idling operation of the engine in which the speed ratio (e) between the pump and the turbine is zero (0), that is, the pump is rotating and the turbine is stopped can be reduced. On the other hand, when the rotation speed of the turbine 42 becomes higher than a predetermined value, the flap 51 and the weight member 51
Since the centrifugal force acting on 1 is increased, as shown in the lower half of FIGS. 4 and 5, the flap 51 has the other end edge pulled and resists the spring force of the coil spring 531 and the pump shell 412 around the support pin 53. Rotate to the side, and the core ring 41
It is positioned on the inner peripheral side of 1. As a result, flap 5
Since the amount of protrusion of No. 1 into the fluid circulation path 400 is small,
Since the circulated working fluid flows into the pump 41 without being substantially affected by the flap 51, the transmission efficiency is not deteriorated during high-speed operation of the engine.

Next, the baffle mechanism 5b in the third embodiment will be described with reference to FIGS. 6 and 7.
The baffle mechanism 5b in the third embodiment is one in which the constituent members of the baffle mechanism 5 in the first and second embodiments are arranged in the pump shell 412. Therefore, in the baffle mechanism 5b in the third embodiment, the same members as those of the baffle mechanisms 5 and 5a in the first embodiment and the second embodiment described above are designated by the same reference numerals, and the description thereof will be omitted. To do. The baffle mechanism 5b in the third embodiment is arranged in the fluid circulation path 400 formed by the pump shell 412 and the turbine shell 422, and one side edge is rotatably supported on the inner peripheral surface of the pump shell 412. Also, a plurality of flaps (six in the illustrated embodiment) are provided. One side edge of the plurality of flaps 51 is rotatably supported by the inner peripheral portion of the pump shell 412. Specifically, a flap supporting member 56 having flap supporting portions 561 and 561 provided at a predetermined interval is attached to the inner peripheral portion of the pump shell 412 by welding, and is attached to one side edge of the flap 51. Is provided with a connecting portion 512. Then, the connecting portion 512 is fitted between the flap supporting portions 561 and 561 of the flap supporting member 56, and the support pins 53 are attached to the flap supporting portions 561, 561 and the connecting portion 512.
The flap 51 is rotatably supported on the inner peripheral portion of the pump shell 412 by inserting the flap 51. The flap 51 supported in this way is formed of, for example, an aluminum alloy, and the weight member 54 made of a metal having a high specific gravity such as copper or lead is joined to the connecting portion 512 by contact. The weight member 54 is arranged on the side opposite to the flap 51 with respect to the support pin 53.

Baffle mechanism 5b in the third embodiment
Corresponds to the centrifugal force acting on the weight member 54 and the plurality of flaps 51. When the rotational speed of the pump 41 is low, the other side edge of the plurality of flaps 51 is connected to the fluid circulation path 400.
Positioned at the center of the turbine 41, the other side edges of the plurality of flaps 51 are attached to the turbine shell 4 when the rotation speed of the pump 41 is high.
It is provided with a restricting means 55 positioned on the inner peripheral side of 22. In the illustrated embodiment, the regulating means 55 includes the weight member 54 mounted on the flap 51 and the pump shell 41.
2 is a spring member composed of a tension coil spring 551 and the like. This tension coil spring 551 is set so that the other side edge of the flap 51 is positioned at the center of the fluid circulation path 400 as shown in the upper half of FIGS. 6 and 7 until the rotational speed of the pump 41 reaches a predetermined value. The load is set.

Baffle mechanism 5b in the third embodiment
Is configured as described above, and the flap 51 is greatly advanced and positioned in the fluid circulation path 400 during the idling operation of the engine in which the rotation speed of the pump 41 is slow. Since the fluid collides and the flow velocity is attenuated, the transmission torque is reduced.
As a result, the drag torque during the idling operation of the engine in which the speed ratio (e) between the pump and the turbine is zero (0), that is, the pump is rotating and the turbine is stopped can be reduced. On the other hand, when the rotation speed of the pump 41 becomes higher than a predetermined value, the centrifugal force acting on the weight member 54 increases, so that the other end edge of the flap 51 acts on itself as shown in the lower half of FIGS. 6 and 7. It rotates around the support pin 53 toward the inner peripheral side of the turbine shell 422 against the centrifugal force and the spring force of the tension coil spring 531. As a result, the fluid circulation path 400 of the flap 51 is
Since the amount of protrusion to the inside is small, the working fluid that circulates flows into the pump 41 without being substantially affected by the action of the flap 51, so that the transmission efficiency does not decrease during high-speed operation of the engine. The baffle mechanism 5b in the third embodiment can be applied to a fluid coupling configured by a pump and a turbine that do not have a core ring.

Next, the baffle mechanism 5c in the fourth embodiment will be described with reference to FIGS. 8 and 9.
The baffle mechanism 5c in the fourth embodiment is one in which the constituent members of the baffle mechanism 5b in the third embodiment are arranged in the turbine shell 422. Therefore, in the baffle mechanism 5c according to the fourth embodiment, the same members as those of the baffle mechanism 5b according to the third embodiment are designated by the same reference numerals, and the description thereof will be omitted. The baffle mechanism 5c in the fourth embodiment is arranged in the fluid circulation path 400 formed by the pump shell 412 and the turbine shell 422, and one side edge is rotatably supported by the inner peripheral portion of the turbine shell 422. A plurality of flaps 51 (six in the illustrated embodiment)
A weight member 54 joined to the connecting portion 512 provided on the flap 51, and a plurality of weight members 54 in a state where the rotation speed of the turbi 42 is low corresponding to the centrifugal force acting on the weight member 54 and the plurality of flaps 51. A tension coil spring 551 or the like that positions the other side edge of the flap 51 at the center of the fluid circulation path 400 and positions the other side edges of the plurality of flaps 51 at the inner peripheral side of the pump shell 412 when the rotational speed of the turby 42 is high. The restriction means 55 is formed of a spring member. In the baffle mechanism 5c according to the fourth embodiment, the flap support portions 561 and 565 provided on the inner peripheral portion of the turbine shell 422 with a predetermined space therebetween.
A flap support member 56 having 61 is attached by welding, and a connecting portion 512 is attached to one side edge of the flap 51.
Is provided. Then, the connecting portion 512 is fitted between the flap supporting portions 561 and 561 of the flap supporting member 56,
The flap 51 is rotatably supported on the inner peripheral portion of the turbine shell 422 by inserting the support pins 53 into the flap support portions 561 and 561 and the connecting portion 512.
Further, in the baffle mechanism 5c according to the fourth embodiment, the tension coil spring 551 as the restricting means 55 is used.
Is disposed between the weight member 54 mounted on the flap 51 and the inner peripheral portion of the turbine shell 422.

Baffle mechanism 5c in the fourth embodiment
Is configured as described above, and until the rotation speed of the turbine 42 reaches a predetermined value (for example, 500 rpm, which is the idling rotation speed of a diesel engine), the tension coil spring as shown in the upper half of FIGS. 8 and 9. The spring force of 531 causes the other side edge of the flap 51 to be positioned at the center of the fluid circulation path 400, and when the rotation speed of the turbine 42 becomes higher than a predetermined value, the centrifugal force acting on the weight member 54 increases, and as shown in FIG. As shown in the lower half of FIG. 9, the flap 51 resists the centrifugal force acting on itself and the spring force of the tension coil spring 531 to support pin 53.
Since it rotates to the inner peripheral side of the pump shell 412 around the center, the same operational effect as the baffle mechanism 5b in the fourth embodiment can be obtained. The baffle mechanism 5c in the fourth embodiment can be applied to a fluid coupling including a pump and a turbine without a core ring.

[0038]

Since the fluid coupling according to the present invention is constructed as described above, it has the following operational effects.

That is, the fluid coupling according to the present invention is arranged in the fluid circulation path formed by the pump shell and the turbine shell, and one side edge thereof is rotated to the core ring of the pump shell or the inner peripheral portion of the core ring of the turbine shell. When the rotational speed of the flap or the turbine that is supported so as to correspond to the centrifugal force acting on the flap is low and the rotational speed of the pump or turbine is low, the other side edge of the flap is positioned at the center of the fluid circulation path and the rotational speed of the pump turbine is high In the state, the baffle mechanism having the other side edge of the flap positioned on the inner peripheral side of the core ring of the turbine shell or the core ring of the pump shell is provided, so that the transmission torque at the time of high speed rotation is reduced. Therefore, the drag torque can be effectively reduced. Further, the fluid coupling according to the present invention includes a flap disposed in a fluid circulation path formed by the pump shell and the turbine shell, and one side edge of which is rotatably supported by an inner peripheral portion of the pump shell or the turbine shell. A weight member that is attached to each flap and that causes the other side edge of the flap to act on the inner peripheral side of the turbine shell or pump shell by the action of centrifugal force, and the rotation speed of the pump or turbine that corresponds to the centrifugal force that acts on the weight member. A baffle having a restricting means for locating the other side edge of the flap at the center of the fluid circulation path in the slow state and for locating the other side edge of the flap at the turbine shell or the inner peripheral portion of the pump shell in the fast state of the pump. Since it has a mechanism, it effectively reduces drag torque without reducing transmission torque at high speed rotation. Door can be.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing an embodiment of a drive device equipped with a fluid coupling constructed according to the present invention.

FIG. 2 is a sectional view showing a first embodiment of a fluid coupling constructed according to the present invention.

3 is a cross-sectional view taken along the line AA in FIG.

FIG. 4 is a cross-sectional view showing a second embodiment of a fluid coupling constructed according to the present invention.

5 is a sectional view taken along line BB in FIG.

FIG. 6 is a sectional view showing a third embodiment of a fluid coupling constructed according to the present invention.

FIG. 7 is a sectional view taken along line CC in FIG.

FIG. 8 is a cross-sectional view showing a fourth embodiment of a fluid coupling constructed according to the present invention.

9 is a cross-sectional view taken along line DD in FIG.

FIG. 10 is a characteristic diagram of a fluid coupling constructed according to the present invention.

FIG. 11 is a characteristic diagram of a conventionally used fluid coupling.

FIG. 12 is an explanatory diagram showing a flow of a working fluid inside a fluid coupling in an example of a conventionally used fluid coupling.

FIG. 13 is an explanatory view showing the flow of the working fluid inside the fluid coupling in another example of the conventionally used fluid coupling.

[Explanation of symbols]

2: Internal combustion engine 21: Crankshaft 4: Fluid coupling 40: Fluid coupling housing 41: Pump 411: Pump coring 412: Pump shell 413: Impeller 5: 42: turbine 421: Turbine coring 422: Turbine shell 423: Lanna 43: Casing 44: Drive plate 45: Ring gear 46: Output shaft 47: Turbine hub 48: Pump hub 5, 5a, 5b, 5c: baffle mechanism 51: Baffle plate 52: flap support member 53: Support pin 54: Weight member 55: Regulatory means 551: tension coil spring 60: Hydraulic pump 62: Pump housing 7: Friction clutch 70: Clutch housing 72: Clutch drive plate 73: Transmission shaft 74: Clutch hub 75: Clutch facing 76: Driven plate 77: Pressure plate 78: Diaphragm spring 79: Release bearing 80: Clutch release fork

Claims (14)

[Claims] 1. A pump having an annular pump shell having an annular core ring, and a plurality of impellers arranged in the pump shell, and an annular core ring arranged so as to face the pump. A fluid coupling comprising an annular turbine shell having the turbine and a turbine having a plurality of runners arranged in the turbine shell, wherein the fluid coupling is arranged in a fluid circulation path formed by the pump shell and the turbine shell. A flap, one side edge of which is rotatably supported on the inner peripheral portion of the core ring of the pump shell, and a centrifugal force acting on the flap, which corresponds to the centrifugal force acting on the flap when the rotational speed of the pump is low. The other side edge is located at the center of the fluid circulation path, and the other side edge of the flap is located on the inner peripheral side of the core ring of the turbine shell when the rotational speed of the pump is high. And a baffle mechanism having a control means. 2. The fluid coupling according to claim 1, wherein a plurality of the flaps are arranged along a core ring of the pump shell. 3. The fluid coupling according to claim 1, wherein a weight member is attached to the other edge portion of the flap. 4. The fluid coupling according to claim 2, wherein the regulating means comprises a spring member arranged between the plurality of flaps and the pump shell. 5. A pump having an annular pump shell having an annular core ring, and a plurality of impellers arranged in the pump shell, and an annular core ring arranged so as to face the pump. A fluid coupling comprising an annular turbine shell having the turbine and a turbine having a plurality of runners arranged in the turbine shell, wherein the fluid coupling is arranged in a fluid circulation path formed by the pump shell and the turbine shell. A flap, one side edge of which is rotatably supported on the inner peripheral portion of the core ring of the turbine shell, and a centrifugal force acting on the flap. The other side edge is located in the center of the fluid circulation path, and the other side edge of the flap is located on the inner peripheral side of the core ring of the pump shell when the rotational speed of the turbine is high. And a baffle mechanism having a regulating means. 6. The fluid coupling according to claim 5, wherein a plurality of the flaps are arranged along a core ring of the turbine shell. 7. The fluid coupling according to claim 5, wherein a weight member is attached to the other edge portions of the several flaps. 8. The fluid coupling according to claim 6, wherein the regulating means includes a spring member arranged between the plurality of flaps and the turbine shell. 9. A pump having an annular pump shell, a plurality of impellers arranged in the pump shell, an annular turbine shell arranged so as to face the pump, and the inside of the turbine shell. A turbine having a plurality of runners disposed in the pump shell, the turbine being disposed in a fluid circulation path formed by the pump shell and the turbine shell, and one side edge of the turbine shell Flaps rotatably supported on the peripheral portion, weight members attached to the plurality of flaps, respectively, for operating the other side edge of the flaps to the inner peripheral side of the turbine shell by the action of centrifugal force, Corresponding to the centrifugal force acting on the weight member, the other side edge of the flap is positioned at the center of the fluid circulation path when the rotation speed of the pump is low, and the flap is located when the rotation speed of the pump is high. Fluid coupling the other side edge of the flop, characterized in that, being provided with a baffle mechanism having a regulating means for positioning the inner peripheral portion of the turbine shell. 10. The fluid coupling according to claim 9, wherein a plurality of the flaps are arranged along the pump shell. 11. The fluid coupling according to claim 9, wherein the restriction means is a spring member arranged between the flap and the pump shell. 12. A pump having an annular pump shell, a plurality of impellers arranged in the pump shell, an annular turbine shell arranged so as to face the pump, and the inside of the turbine shell. A turbine having a plurality of runners disposed in the turbine shell, the turbine being disposed in a fluid circulation path formed by the pump shell and the turbine shell, and having one side edge of the turbine shell. A flap rotatably supported on the circumference, a weight member attached to each of the plurality of flaps, and a weight member for actuating the other side edge of the flap to the inner circumference side of the pump by the action of centrifugal force; Corresponding to the centrifugal force acting on the member, the other side edge of the flap is positioned at the center of the fluid circulation path when the rotational speed of the pump is low, and the flap is fast when the rotational speed of the pump is high. And comprising a baffle mechanism having a regulating means for positioning the other side edge on the inner peripheral portion of the pump shell, a fluid coupling, characterized in that. 13. The fluid coupling according to claim 12, wherein a plurality of the flaps are arranged along the turbine shell. 14. The fluid coupling according to claim 13, wherein the regulating means includes a spring member arranged between the plurality of flaps and the turbine shell.