JP2015110975A - Oil passage structure of hydraulic power transmission apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil passage structure capable of realizing both fusion resistance related to a bearing bush of a pump impeller and prevention of reduction in the quantity of torque converter hydraulic oil.SOLUTION: A seal ring 34 restricts leakage of α-direction hydraulic oil toward a torque converter via an oil passage part 32a on one end of a bush 31, in a β-direction via an oil passage part 32b on the other end of the bush 31, and a leakage quantity β of the hydraulic oil is made to correspond to a quantity of oil required to lubricate a bearing surface (inner circumferential surface) of the bush 31. This can supply the hydraulic oil of the quantity required for lubrication onto the bearing surface of the bush 31 and compensate for fusion resistance of the bush 31. On the other hand, the restriction of the leakage quantity β of the hydraulic oil can prevent the hydraulic oil α toward the torque converter via the oil passage part 32b on one end of the bush 31 from being reduced to an unignorable degree. It is, therefore, possible to realize the fusion resistance of the bush 31 and the prevention of the reduction in the torque converter hydraulic oil.

Description

  The present invention relates to an improvement in an oil passage structure that supplies a working fluid to a fluid transmission device such as a torque converter.

  In general, a fluid transmission device (torque converter) has an input element (pump impeller) driven by a power source and an output element (turbine runner) driven by the input element via a working fluid coaxially arranged opposite to each other. Therefore, supply of working fluid (working oil) is indispensable, and the oil passage structure for that purpose has been conventionally configured as described in Patent Document 1, for example.

  First, the support structure of the fluid transmission device (torque converter) will be described. When supporting the fluid transmission device (torque converter), the input element (pump impeller) is fixed to the fixed shaft (automatic transmission) by the bush in the sleeve that rotates with the input element (pump impeller). In the machine, the input shaft (pump impeller) is coupled to a power source (engine) while being rotatably supported on a hollow fixed shaft coupled to the transmission case so as to wrap around the input shaft, Rotating support of the fluid transmission device (torque converter).

  The oil passage structure for supplying the working fluid (hydraulic oil) to the fluid transmission device (torque converter) includes an oil passage portion on one end side corresponding to the bush among the annular oil passage between the sleeve and the fixed shaft. It has been a common practice to supply the working fluid (hydraulic oil) to the fluid transmission device (torque converter) through the above.

JP 2005-325979 A

  However, the oil passage structure of the conventional fluid transmission device is based on the premise that the bush does not leak the working fluid from the oil passage portion on one end side of the bush toward the oil passage portion on the other end side on the bearing surface. Therefore, since no countermeasure was taken for the oil passage portion on the other end side of the bush, it was confirmed that the following problems occurred.

  In particular, when the working fluid deteriorates or becomes hot and the viscosity of the working fluid decreases, the working fluid passes through the bearing surface of the bush and from the oil passage portion on one end side of the bush to the other end side. Leakage tends to occur toward the oil passage, and the amount of leakage increases to cause the following problems.

The working fluid of the fluid transmission device is usually directed to the oil cooler after being used for the operation of the fluid transmission device, and after cooling by this, each lubrication (cooling) request point (in the case of an automatic transmission, a bearing, a speed change friction element, etc.) ) To be used for lubrication (cooling) of these parts.
By the way, as described above, when a large amount of working fluid leaks from the oil passage portion on one end side of the bush to the oil passage portion on the other end side through the bush, the amount of working fluid directed to the oil cooler by the amount of the leakage There is a concern that the cooling by the oil cooler will decrease and the working fluid temperature of the fluid transmission (automatic transmission) will rise to a problem.

Such a rise in the working fluid temperature adversely affects not only the fluid transmission device but also the durability of an automatic transmission or the like using the fluid transmission device. Therefore, measures to eliminate this concern are required.
For this measure, it is necessary to increase the cooling capacity of the oil cooler, increase the oil cooler, or switch to fail-safe operation that suppresses the temperature rise when the working fluid temperature rises. The cost disadvantage is unavoidable, and the latter measure causes a new problem that the driving performance is sacrificed.

  Further, when a large amount of working fluid leaks from the oil passage portion on one end side of the bush toward the oil passage portion on the other end side through the bearing surface of the bush, the working fluid amount of the fluid transmission device is increased by the amount of the leakage. As a result, the transmission response performance of the fluid transmission device is reduced, and the lockup region is reduced (transmission efficiency is reduced) due to the influence on the direct connection (lockup) control between the input and output elements.

  The present invention is based on the above fact recognition, and the lubrication (cooling) of the bush that is essential is negligible if the amount of leakage of the working fluid that leaks through the oil passage portion on the other end side of the bush becomes zero. From the viewpoint that it is necessary to achieve both seizure resistance of the bush and prevention of a decrease in the amount of working fluid to the fluid transmission device, the fluid transmission device capable of solving the above problems while realizing this compatibility. An object is to provide an oil passage structure.

For this purpose, the oil passage structure of the fluid transmission according to the present invention is constituted as follows.
First, in order to explain the oil passage structure of the fluid transmission device which is the premise of the present invention,
A fluid transmission device in which an input element driven by a power source and an output element fluid-driven by the input element via a working fluid are coaxially arranged opposite to each other,
The fluid transmission device is rotatably supported by supporting the input element on a fixed shaft by a bush in a sleeve that rotates together with the input element, and the bush among the annular oil passages between the sleeve and the fixed shaft. The working fluid is supplied to the fluid transmission device through an oil passage portion on one end side of the fluid transmission device.

The present invention provides an oil passage structure of such a fluid transmission device,
The working fluid heading toward the fluid transmission device through the oil passage portion on one end side of the bush is restricted from leaking through the oil passage portion on the other end side of the bush among the annular oil passage between the sleeve and the fixed shaft. It is characterized by the structure which provided the seal ring to perform in the oil-path part in this other end side.

In the oil passage structure of the fluid transmission device according to the present invention described above,
In order to restrict the working fluid that is directed to the fluid transmission device through the oil passage portion on one end side of the bush through the oil passage portion on the other end side of the bush by the seal ring,
The amount of working fluid leaking through the oil passage at the other end of the bush does not become zero, and the amount of working fluid corresponding to this leakage passes from the oil passage at one end of the bush through the bush. The bush can be lubricated (cooled) by moving to the oil passage part on the end side, and the seizure resistance of the bush can be compensated.
By limiting the amount of working fluid leaking through the oil passage at the other end of the bush, the amount of working fluid going to the fluid transmission device through the oil passage at the one end of the bush is prevented from becoming a problem. Can
It is possible to achieve both seizure resistance of the bush and prevention of reduction of the working fluid amount to the fluid transmission device.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a longitudinal side view showing a state where a torque converter having an oil passage structure according to a first embodiment of the present invention is used in an automatic transmission. FIG. 2 is an enlarged detail cross-sectional view of a main part showing an oil passage structure in the torque converter in FIG. FIG. 5 is a front view showing a modification of the seal ring used in the oil passage structure of FIGS. FIG. 3 is an enlarged detail cross-sectional view of a main part similar to FIG. 2, showing an oil passage structure according to a second embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
<Configuration of the first embodiment>
FIG. 1 shows a fluid transmission device having an oil passage structure according to a first embodiment of the present invention. In this embodiment, the fluid transmission device is configured as a torque converter 11, and the torque converter 11 is an automatic transmission 12. The transmission input shaft 13 is connected to the output shaft (crankshaft) of an engine (power source) (not shown) coaxially arranged at the protruding end on the right side of the input shaft 13 in the drawing.

14 is a transmission case of the automatic transmission 12, and the opening end of the transmission case 14 is closed with a pump cover 15.
Further, a converter housing 16 is attached to the opening end of the transmission case 14 so as to be coaxial with the opening, and the torque converter 11 is accommodated in the converter housing 16.
An oil pump 17 is interposed between the torque converter 11 and the pump cover 15. As the oil pump 17, an internal gear pump in which an inner gear 17in and an outer gear 17out are meshed with each other is used. The inner gear 17in and the outer gear 17out Is housed in a space defined between the pump cover 15 and a pump housing 18 coaxially attached to the pump cover 15.

A hollow fixed shaft 19 (fixed shaft) is fitted into the center hole of the pump cover 15 to integrate them, and as a result, the hollow fixed shaft 19 is integrally coupled to the transmission case 14.
The hollow fixed shaft 19 extends from the pump cover 15 through the pump housing 18 and protrudes into the converter housing 16.
A transmission input shaft 13 of a transmission gear mechanism (not shown) housed in the transmission case 14 passes through the hollow fixed shaft 19 so as to freely rotate, and the tip of the transmission input shaft 13 enters the converter housing 16. Make it protrude.

The torque converter 11 housed in the converter housing 16 is disposed and supported on the hollow fixed shaft 19 as described below, and is disposed on the tip of the transmission input shaft 13 for driving connection.
Here, the torque converter 11 mainly includes a pump impeller 11p as an input element, a turbine runner 11t as an output element, and a stator 11s as a reaction force element.

The pump impeller 11p and the turbine runner 11t are disposed coaxially and face each other, and a stator 11s is interposed between opposed inner peripheral portions of the pump impeller 11p and the turbine runner 11t.
The pump impeller 11p is rotatably supported on the hollow fixed shaft 19 via a sleeve 21 attached to the center of the left end in the figure, and via a converter cover 22 attached to the right end opening in the figure so as to close the opening. Coupled to an engine crankshaft (not shown).
The turbine runner 11t is rotationally engaged with the tip of the transmission input shaft 13, and the stator 11s is placed on the hollow fixed shaft 19 via the one-way clutch 23 so as not to rotate in the reverse direction to the engine.

The end of the sleeve 21 on the side far from the turbine runner 11t is rotationally engaged with the inner gear 17in of the oil pump 17, and drives the oil pump 17 (inner gear 17in) through the pump impeller 11p.
The oil pump 17 sucks the hydraulic oil (working fluid) stored in the lower oil pan of the automatic transmission 12 and discharges the hydraulic oil to a shift control unit and a lubrication request location.
The hydraulic oil (working fluid) is then directed to the torque converter 11 through an oil passage 24 including an annular space between the transmission input shaft 13 and the hollow fixed shaft 19, and the hydraulic oil flowing through the torque converter 11 is input to the transmission. It goes to an oil cooler (not shown) through an oil passage 25 including the central hole of the shaft 13, and is cooled here and then returned to the lower oil pan of the automatic transmission 12.

  The torque converter 11 causes the internal working fluid to collide with the turbine runner 11t by centrifugal force by the engine driven pump impeller 11p, and then returns the working fluid to the pump impeller 11p under the guidance of the stator 11s. As the torque increases, the engine rotation can be transmitted from the pump impeller 11p to the turbine runner 11t and the transmission input shaft 13 while absorbing torque fluctuations. (Converter state)

The torque converter 11 is a lock capable of directly connecting the pump impeller 11p as an input element and the turbine runner 11t as an output element in order to increase transmission efficiency in a situation where the above torque increasing function and torque fluctuation absorbing function are not required. Built-in up clutch piston 26.
The lockup clutch piston 26 is rotationally coupled to the turbine runner 11t via a torsional damper 27, but is displaceable in the axial direction.
The lockup clutch piston 26 is arranged so as to face the converter cover 22, and divides the inside of the torque converter 11 into a lockup chamber 28 and a converter chamber 29 between the lockup clutch piston 26 and the converter cover 22.

Of the oil passages 24 and 25, the oil passage 24 communicates with the converter chamber 29, and the oil passage 25 communicates with the lockup chamber 28.
When the amount of oil flowing out from the lockup chamber 28 via the oil passage 25 is limited, the lockup chamber 28 and the converter chamber 29 on both sides of the lockup clutch piston 26 have the same pressure, and the lockup clutch piston 26 becomes the converter cover. The torque converter 11 is operated in the converter state without being directly connected between the pump impeller 11p and the turbine runner 11t.
When the amount of oil flowing out from the lockup chamber 28 through the oil passage 25 is not limited, the lockup clutch piston 26 is pressed against the converter cover 26 by the dynamic pressure of the hydraulic oil and directly connects the pump impeller 11p and the turbine runner 11t. Thus, the torque converter 11 is operated in the lock-up state.

<Oil channel structure of torque converter>
The oil passage structure for supplying hydraulic oil to the torque converter 11 will be described in detail below with reference to FIGS.

When the torque converter 11 (pump impeller 11p) is supported on the hollow fixed shaft 19, the bush 31 is placed in the annular space between the sleeve 21 and the hollow fixed shaft 19 connected to the center of the left end of the pump impeller 11p in the figure. Is provided.
The bush 31 is configured such that the inner peripheral surface is slidably fitted to the outer peripheral surface of the hollow fixed shaft 19 so that the inner peripheral surface is a bearing surface, and the outer peripheral surface is fitted to the inner peripheral surface of the sleeve 21, thereby The impeller 11p is rotatably supported on the hollow fixed shaft 19.

  The bush 31 is an oil passage on one end side of the bush 31 near the pump impeller 11p in the annular oil passage 32 between the sleeve 21 and the hollow fixed shaft 19, as indicated by an arrow α in FIG. It arrange | positions in the position which is supplied to the torque converter 11 (converter chamber 29) through the part 32a.

Of the annular oil passage 32 between the sleeve 21 and the hollow fixed shaft 19, a seal ring 34 is provided in the oil passage portion 32b on the other end side of the bush 31 far from the pump impeller 11p, and the seal ring 34 is fixed hollow. Positioned by engaging with the outer periphery of the shaft 19.
This seal ring 34 has a hydraulic oil amount that hydraulic oil that goes to the torque converter 11 (converter chamber 29) through the oil passage portion 32a on one end side of the bush 31 leaks through the oil passage portion 32b on the other end side of the bush 31. Rather than set to 0, it has a sealing ability that allows a certain amount of hydraulic fluid to leak as shown by arrow β in Fig. 2 and limits the amount of hydraulic fluid to meet the following requirements: And

  Here, the allowable amount of the leaking hydraulic oil indicated by the arrow β in FIG. 2 corresponds to the required lubricating oil amount (for example, 50 cc / min) of the bush 31 (inner peripheral lubrication surface). An amount of hydraulic oil corresponding to the lubrication requirement can flow from the passage portion 32a to the bearing surface (inner peripheral surface) of the bush 31.

  When the seal ring 34 is configured so that the hydraulic oil can be leaked as indicated by the arrow β in FIG. 2, the seal ring 34 is formed in a continuous annular shape, and the space between the outer peripheral surface and the inner peripheral surface of the sleeve 21 is The outer diameter of the seal ring 34 is set to the inner peripheral surface of the sleeve 21 so that the clearance (the amount of hydraulic oil leakage) in the cylinder corresponds to the required lubricating oil amount (for example, 50 cc / min) of the bush 31 (inner peripheral lubricating surface). In the context of

Instead, as shown in FIG. 3, the seal ring 34 is configured in a discontinuous ring shape with a circumferential portion 34a cut out, and the width of the cutout portion 34a is determined by the amount of hydraulic oil leaking from here. May be determined so as to correspond to the required amount of lubricating oil of the bush 31 (inner peripheral lubricating surface).
In this case, the workability when the seal ring 34 is engaged with the outer periphery of the hollow fixed shaft 19 is improved, which is convenient.

In any case, in this embodiment, the seal ring 34 is preferably made of a material having a larger thermal expansion coefficient than that of the sleeve 21.
In this case, the difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 (the amount of hydraulic oil leakage) is smaller when the oil temperature is high, and the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 decrease as the oil temperature decreases. (The amount of hydraulic oil leakage) increases.

By the way, the viscosity of the hydraulic oil decreases as the temperature of the hydraulic oil increases, and the amount of hydraulic oil leakage increases. At this high oil temperature, the difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 (hydraulic oil leakage oil) By reducing the amount), it is possible to prevent the amount of hydraulic oil leakage from increasing at high oil temperatures.
Conversely, when the hydraulic oil temperature is low, the viscosity increases and the amount of hydraulic oil leakage becomes insufficient. At this low oil temperature, the difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 (hydraulic oil leakage) By increasing the oil amount), it is possible to prevent the amount of hydraulic oil leakage from becoming insufficient at low oil temperatures.

  That is, when the seal ring 34 is made of a material having a thermal expansion coefficient larger than that of the sleeve 21, the amount of hydraulic oil leakage is always equal to the required amount of lubricating oil (for example, 50cc) of the bush 31 (inner peripheral lubrication surface) regardless of the oil temperature change. / Min).

In this embodiment, further, a bush lubrication path 35 for guiding a part of the hydraulic oil from the oil path 24 toward the oil path portion 32a on one end side of the bush 31 to the inner peripheral surface (bearing surface) of the bush 31 is provided with the hollow fixed shaft 19 Provided.
In this embodiment, the bush lubrication path 35 is a radial through hole extending from the inner peripheral surface of the hollow fixed shaft 19 to the outer peripheral surface of the hollow fixed shaft 19 with which the inner peripheral surface (bearing surface) of the bush 31 is fitted. Configure.

<Effect of the first embodiment>
In the oil passage structure of the torque converter 11 according to the above-described embodiment, the hydraulic oil that travels toward the torque converter 11 (converter chamber 29) via the oil passage portion 32a on one end side of the bush 31 is transferred to the other end of the bush 31. The leakage through the oil passage portion 32b on the side is limited by the seal ring 34, and the hydraulic oil leakage flow rate from the seal ring 34 is reduced to the required lubricating oil amount (for example, 50 cc / min) of the bush 31 (inner peripheral lubrication surface). Because we made it correspond
An amount of hydraulic fluid corresponding to the lubrication requirement can flow from the oil passage portion 32a on one end side of the bush 31 to the bearing surface (inner peripheral surface) of the bush 31, and the bush 31 can be lubricated (cooled). The seizure resistance of the bush 31 can be compensated.

In addition, according to the oil passage structure of the present embodiment, the torque converter passes through the oil passage portion 32a on one end side of the bush 31 due to the restriction of the amount of hydraulic oil leaking through the oil passage portion 32b on the other end side of the bush 31. It is possible to prevent the amount of working fluid heading 11 (converter chamber 29) from decreasing so as to become a problem.
As described above, according to the oil passage structure of the present embodiment, it is possible to achieve both seizure resistance of the bush 31 and prevention of reduction in the amount of working fluid to the torque converter 11.

Further, in the oil passage structure of the present embodiment, as shown in FIG. 3, the seal ring 34 is formed in a discontinuous ring shape with a circumferential portion 34a cut out, and the width of the cutout portion 34a is set here. The amount of hydraulic oil that leaks out from the bush is determined to correspond to the amount of lubricating oil required for the bush 31 (inner lubrication surface).
In addition to being able to achieve the above actions and effects as they are, the seal ring 34 can be engaged with the outer periphery of the hollow fixed shaft 19 while being elastically deformed in the diameter increasing direction. Can be improved.

In the oil passage structure of the present embodiment, since the seal ring 34 is made of a material having a larger thermal expansion coefficient than the sleeve 21,
The difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 (the amount of hydraulic oil leakage) is smaller as the oil temperature rises, and the difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 as the oil temperature decreases. (The amount of hydraulic oil leakage) becomes large, and the following effects can be achieved.

In other words, the viscosity of the hydraulic oil decreases as the oil temperature rises and the amount of oil leaked increases. At this high oil temperature, the difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 (hydraulic oil leakage oil) Therefore, it is possible to prevent the amount of hydraulic oil leakage from increasing at a high oil temperature.
Conversely, when the hydraulic oil temperature is low, the viscosity increases and the amount of hydraulic oil leakage becomes insufficient. At this low oil temperature, the difference between the outer diameter of the seal ring 34 and the inner diameter of the sleeve 21 (hydraulic oil leakage) Since the amount of oil) increases, it is possible to prevent the amount of hydraulic oil leakage from becoming insufficient at low oil temperatures.
Therefore, in the present implementation in which the seal ring 34 is made of a material having a larger thermal expansion coefficient than the sleeve 21, the amount of hydraulic oil leakage is always the required lubricating oil of the bush 31 (inner peripheral lubrication surface) regardless of the oil temperature change. It can correspond to the amount (for example, 50 cc / min).

  In this embodiment, the bush 31 is further provided with a bush lubrication path 35 that guides a part of the hydraulic oil from the oil path 24 toward the oil path portion 32a on one end side of the bush 31 to the inner peripheral surface (bearing surface) of the bush 31. Thus, the lubrication (cooling) of the bush 31 can be further ensured, and the seizure resistance of the bush 31 can be further improved.

<Second embodiment>
FIG. 4 shows the oil passage structure of the torque converter 11 according to the second embodiment of the present invention. In this embodiment, the seal ring 34 is engaged with the inner peripheral surface of the sleeve 21.
In this case, the seal ring 34 is configured in a discontinuous annular shape with the notch 34a described above with reference to FIG. 3, and the seal ring 34 is fitted into the inner peripheral surface of the sleeve 21 in a reduced diameter state and slid in the axial direction. In this manner, the sleeve 21 is engaged and positioned in a groove provided on the inner peripheral surface of the sleeve 21.

<Effect of the second embodiment>
Other than that, the configuration is the same as that of the first embodiment described above. In this embodiment, the same operation and effect as in the first embodiment can be achieved, and the seizure resistance of the bush 31 and the torque converter can be achieved. Therefore, it is possible to achieve both the prevention of decrease in the amount of working fluid to 11.

In this embodiment, the seal ring 34 is formed in a discontinuous annular shape with the notch 34a described above with reference to FIG. 3, and the seal ring 34 is fitted into the inner peripheral surface of the sleeve 21 in a reduced diameter state. In order to engage in the groove provided on the inner peripheral surface of the sleeve 21 while sliding in the direction,
Even if the seal ring 34 is engaged in the inner circumferential groove of the sleeve 21, this engagement operation does not become difficult.

  Further, since the seal ring 34 is engaged with the inner peripheral surface of the sleeve 21, the seal ring 34 can follow the axial displacement and expansion / contraction of the torque converter 11, and also due to the axial displacement and expansion / contraction of the torque converter 11. The seal ring 34 does not impair the oil leakage control at all, and the above-mentioned operation and effect can be maintained for a long time.

<Other examples>
In the above description, the description has been made on the assumption that the fluid transmission device is the torque converter 11. However, the idea of the present invention can be similarly applied to fluid transmission devices other than the torque converter to achieve the same operation and effect. Needless to say.

11 Torque converter (fluid transmission)
11p Pump impeller (input element)
11t turbine runner (output element)
11s stator (reaction element)
12 Automatic transmission
13 Transmission input shaft
14 Transmission case
15 Pump cover
16 Converter housing
17 Oil pump
18 Pump housing
19 Hollow fixed shaft (fixed shaft)
21 sleeve
22 Converter cover
23 One-way clutch
24,25 Oilway
26 Lock-up clutch piston
27 Torsional damper
28 Lock-up room
29 Converter room
31 Bush
32 annular oil passage
32a Oil passage on one end
32b Oil passage on the other end
34 Seal ring
35 Bush lubrication path

Claims (7)

A fluid transmission device in which an input element driven by a power source and an output element fluid-driven by the input element via a working fluid are coaxially arranged opposite to each other,
The fluid transmission device is rotatably supported by supporting the input element on a fixed shaft by a bush in a sleeve that rotates together with the input element, and the bush among the annular oil passages between the sleeve and the fixed shaft. In the oil passage structure of the fluid transmission device configured to supply the working fluid to the fluid transmission device via the oil passage portion on one end side of the
The working fluid heading toward the fluid transmission device through the oil passage portion on one end side of the bush is restricted from leaking through the oil passage portion on the other end side of the bush among the annular oil passage between the sleeve and the fixed shaft. An oil passage structure for a fluid transmission device, characterized in that a seal ring is provided in an oil passage portion on the other end side. In the oil passage structure of the fluid transmission device according to claim 1,
The fluid transmission is characterized in that the seal ring has a sealing ability so that a working fluid of an amount corresponding to a lubrication requirement can flow from an oil passage portion on the one end side to a bearing surface of the bush. The oil passage structure of the device. In the oil passage structure of the fluid transmission device according to claim 1 or 2,
The seal ring is configured to be discontinuous by cutting out a part in a circumferential direction, and configured to allow leakage of the working fluid through the notch. Oil passage structure. In the oil passage structure of the fluid transmission device according to any one of claims 1 to 3,
The oil ring structure of a fluid transmission device, wherein the seal ring is fitted to an outer periphery of the fixed shaft. In the oil passage structure of the fluid transmission device according to claim 4,
The oil passage structure of a fluid transmission device, wherein the seal ring has a thermal expansion coefficient larger than that of the sleeve. In the oil passage structure of the fluid transmission device according to any one of claims 1 to 3,
The oil passage structure of a fluid transmission device, wherein the seal ring is fitted to the inner periphery of the sleeve. In the oil passage structure of the fluid transmission device according to any one of claims 1 to 6,
An oil passage structure of a fluid transmission device, characterized in that a bush lubrication passage is provided for guiding a part of the working fluid toward the oil passage portion on the one end side to a bearing surface of the bush.

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