JP2001159458A - Torque converter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a torque ratio and transmission efficiency from being degraded, even when discharge pressure of an oil pump is markedly decreased to the atmospheric pressure, in a torque converter. SOLUTION: A gap g2 between bosses 11a, 12a of a turbine impeller 11 and a stator impeller 12 is substantially closed, an oil inlet 30 is formed between the bosses 10a, 12a of a pump impeller 10 and the stator impeller 12, and discharge oil of an oil pump 27 is supplied from only the oil inlet 30 to a torque converter T.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a torque converter and, more particularly, to a pump in which bosses of a pump impeller and a turbine impeller are opposed to each other on both sides of a stator impeller with a gap therebetween. The present invention relates to an improvement in a torque converter in which a peripheral side communicates with a supply oil passage connected to an oil pump, and an oil outlet is provided in an oil chamber formed on the back side of the turbine impeller and communicating between the pump impeller and the turbine impeller.

[0002]

2. Description of the Related Art Such a torque converter is already known, for example, as disclosed in Japanese Patent Application Laid-Open No. 5-230303.

[0003]

In such a conventional torque converter, a gap on both sides of the boss of the stator impeller serves as an oil inlet, and oil discharged from an oil pump is supplied into the torque converter through both gaps. It is supposed to be.

However, during torque amplification, a large pressure difference is generated between the inlet and the outlet of the stator impeller due to the pressure drop when the oil passes through the stator impeller. If the pressure drops significantly, air bubbles are generated in the oil at the exit of the stator impeller where the pressure is lowest, and the oil that has exited the turbine impeller flows out of the gap between the boss of the turbine impeller and the stator impeller. As a result, the torque ratio and the transmission efficiency may be greatly reduced.

The present invention has been made in view of such circumstances, and has as its object to provide the above-described torque converter that can avoid the above-described problems even when the discharge pressure of the oil pump is significantly reduced. I do.

[0006]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a boss of a stator impeller in which both bosses of a pump impeller and a turbine impeller are opposed to both sides of a boss of a stator impeller. In a torque converter in which a supply oil passage communicating with an oil pump communicates with the inner peripheral side of the oil pump and an oil outlet is provided in an oil chamber formed on the back side of the turbine impeller and communicating between the pump impeller and the turbine impeller, An oil that substantially closes a gap between the bosses of the wheel and the stator impeller and communicates at least one of the bosses of the pump impeller and the stator impeller with the inner peripheral side of the boss of the stator impeller to an outlet of the stator impeller. The first feature is that an entrance is provided.

According to the first feature, when a large pressure difference is generated between the inlet and the outlet of the stator impeller, the total amount of oil discharged from the oil pump is reduced even if the discharge pressure of the oil pump is significantly reduced. Since the oil is supplied from the oil inlet to the outlet of the stator impeller, a decrease in the outlet pressure can be effectively suppressed, and generation of bubbles in the oil can be prevented.
On the other hand, the oil leaving the turbine impeller does not flow out between the bosses of the turbine impeller and the stator impeller.
All of it can pass through the stator impeller.
Thus, a decrease in the torque ratio and the transmission efficiency is suppressed.

Further, in addition to the first feature, the present invention provides the oil inlet between a pump impeller and a stator impeller boss which is larger than the narrowed gap between the bosses of the turbine impeller and the stator impeller. The second feature is that the gap is formed.

According to the second feature, the simple structure can contribute to preventing the torque ratio and the transmission efficiency from lowering.

Further, in the present invention, in addition to the first feature, the oil inlet is constituted by a radial groove formed on at least one of the opposing surfaces of the bosses of the turbine impeller and the stator impeller. Features.

According to the third feature, it is also possible to simplify the configuration and prevent the torque ratio and the transmission efficiency from being lowered.

Further, in the present invention, in addition to the first feature, a fourth feature is that the oil inlet is constituted by a through hole formed in a boss of the pump impeller.

[0013] According to the fourth feature, it is possible to simplify the configuration and prevent the torque ratio and the transmission efficiency from decreasing.

Further, according to the present invention, in addition to any one of the first to fourth features, an annular seal member is interposed between the opposing surfaces of the boss of the turbine impeller and the stator impeller. The feature of.

According to the fifth feature, since the gap between the bosses of the turbine impeller and the stator impeller is sealed by the seal member, the inflow and outflow of oil through the gap is reliably prevented, and the torque ratio is reduced. Also, it is possible to contribute to prevention of reduction in transmission efficiency.

[0016]

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 of a torque converter showing a first embodiment of the present invention, FIG. 2 is an enlarged view of a part of FIG. 1, and FIG. 3 shows a second embodiment of the present invention, corresponding to FIG. FIG. 4 shows a third embodiment of the present invention, an enlarged view corresponding to FIG. 2, FIG. 5 shows a fourth embodiment of the present invention, an enlarged view corresponding to FIG. 2, and FIG. FIG. 4 is a characteristic diagram of the torque converter of the invention.

First, a description will be given of the first embodiment of the present invention shown in FIGS. In FIG. 1, a drive gear 4a, a torque converter T, and a transmission clutch Cc of a primary reduction gear 4 are mounted on a crankshaft 2 supported on a crankcase 1 of an engine via a bearing 3 from the right outer side of the crankcase 1. The output of the crankshaft 2 is sequentially transmitted to the input shaft of a multi-stage transmission (not shown) via the transmission clutch Cc, the torque converter T, and the primary reduction gear 4.

As shown in FIGS. 1 and 2, the torque converter T includes a pump impeller 10, a turbine impeller 11, and a stator impeller 12. Pump impeller 10
Is disposed adjacent to the transmission clutch Cc, and a boss 10a formed at the center of the pump impeller 10 has a gap g1 on the right side of the boss 12a formed at the center of the stator impeller 12. At the same time, it is supported on the crankshaft 2 via the needle bearing 13.

A transmission plate 15 is fixed to the outer surface of the pump impeller 10 so as to engage with the output of the transmission clutch Cc. Therefore, the output torque of the transmission clutch Cc is transmitted to the pump impeller 10 via the transmission plate 15.
The shift clutch Cc is controlled to be in an off state to avoid a shift shock when a multi-stage transmission (not shown) is switched.

On the crankshaft 2, a pump impeller 1 is provided.
A cylindrical stator shaft 20 is disposed between the boss 10a of the stator shaft 20 and the ball bearing 3 supporting the crankshaft 2, and a dog 20a formed at the right end of the stator shaft 20 is provided.
Is engaged with a notch 40 formed on the inner periphery of the boss 12 a of the stator impeller 12. Thus, the stator shaft 20 is connected to the stator impeller 12. This stator shaft 20
The right end is supported by the crankshaft 2 via a needle bearing 14 so as to be relatively rotatable. Stator shaft 20
A stator arm plate 16 is fixed to the left end of
Cylindrical part 16 that this stator arm plate 16 has in the middle
The outer peripheral surface of “a” is supported on the crankcase 1 via the ball bearing 17. An outer peripheral portion of the stator arm plate 16 is supported by the crankcase 1 via a freewheel 18.

A boss 11a fixed to the center of the turbine impeller 11 has a needle bearing 21
, And is opposed to the left end surface of the boss 12a of the stator impeller 12 with a gap g2 therebetween.

A turbine shaft 19 is integrally connected to a boss 11a of the turbine impeller 11, and a left end of the turbine shaft 19 is supported on the inner peripheral surface of the cylindrical portion 16a of the stator arm plate 16 via a ball bearing 22. A one-way clutch 24 is provided between the turbine shaft 19 and the crankshaft 2 through a lateral hole 23 of the stator shaft 20. The one-way clutch 24 is turned on when a reverse load is applied to the turbine shaft 19, so that the turbine shaft 19 and the crankshaft 2 are directly connected.

A drive gear 4a of the primary reduction gear 4 is integrally formed on the outer periphery of the left end portion of the turbine shaft 19, and a driven gear 4b provided on an input shaft of the transmission is meshed with the drive gear 4a. The primary reduction gear 4 configured as described above is disposed between the crankcase 1 and the torque converter T.

The pump impeller 10 includes a turbine impeller 11
And a side cover 26 that covers the outer surface of the turbine impeller 11 is oil-tightly fitted to the open end of the extension 10b. The side cover 26 is fitted to the outer peripheral surface of the turbine shaft 19 so as to be relatively rotatable. By the side cover 26, an oil chamber 41 communicating between the pump impeller 10 and the turbine impeller 11 is defined on the back side of the turbine impeller 11.

The axial position of the pump impeller 10 is such that the push plate 42 fixed to the intermediate step 2a of the crankshaft 2 is
The axial position of the turbine impeller 11 is determined by the ball bearing 17 that supports the turbine shaft 19. The axial position of the stator impeller 12 is such that the inner peripheral end of the boss 12a is positioned at the inner race 13 of the needle bearings 13, 14.
a, 14a. that time,
Boss 11 of turbine impeller 11 and stator impeller 12
The gap g2 between the holes a and 12a is set as small as possible so that the oil does not easily flow. On the other hand, the bosses 10a, 12a of the pump impeller 10 and the stator impeller 12 are provided.
The gap g1 between them is set to be sufficiently large so that oil can easily flow therethrough, and serves as the oil inlet 30.

The crankshaft 2 is provided with an upstream supply oil passage 25a opening at the right end face thereof and a downstream supply oil passage 25b connected to a lubricating portion around the crankshaft 2.
5a, an oil pump 27 driven by the crankshaft 2 pumps oil sucked from an oil reservoir 28. The oil reservoir 28 is formed at the bottom of the crankcase 1.

The upstream supply oil passage 25 is connected to the crankshaft 2.
An inlet hole 32 is formed, which communicates a with the inner peripheral surface of the boss 12 a of the stator impeller 12. Therefore, this inlet hole 32
Communicates with the oil inlet 30 through the notch 40 of the boss 12a.

The turbine shaft 19 is provided with an oil outlet 31 connected to the oil chamber 41 on the rear side of the turbine impeller 11.
3 communicates with the downstream supply oil passage 25b through an outlet hole 34 formed in the crankshaft 2.

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

When the oil pump 27 driven by the crankshaft 2 feeds oil to the upstream supply oil passage 25a of the crankshaft 2 during operation of the engine, the oil first flows into the inlet 32, the notch 40 and the oil inlet 30. , Flows into the torque converter T, fills the space between the pump impeller 10 and the turbine impeller 11, further fills the oil chamber 41, and then moves from the oil outlet 31 to the side hole 23 to lubricate the one-way clutch 24, Then, through the outlet hole 34, the crankshaft 2
Flows to the downstream supply oil passage 25b for lubrication around the crankshaft 2. In this way, the oil in the torque converter T is replaced by a new one, and the oil is cooled.

When the rotation of the crankshaft 2 is transmitted to the pump impeller 10 due to the on state of the transmission clutch Cc, the oil in the torque converter T is released by the rotation of the pump impeller 10. The rotation torque of the pump impeller 10 is transmitted to the turbine impeller 11 while circulating in the torque converter T like the turbine impeller 11 → stator impeller 12 → pump impeller 10. At this time, the pump impeller 10 and the turbine impeller 1
If the torque amplifying action occurs between the stator impellers 1, the reaction force accompanying the torque is applied to the stator impeller 12, and the stator impeller 1
2 is fixedly supported on the crankcase 1 by the locking action of the freewheel 18.

In this case, the pressure of the oil flowing from the turbine impeller 11 to the pump impeller 10 is converted into kinetic energy in the stator impeller 12, and accordingly, a relatively large pressure is applied between the inlet and the outlet of the stator impeller 12. A difference occurs. At this time, the pressure relationship of each part of the torque converter T is as follows.

P1>P2> P3 where P1: outlet pressure of the pump impeller P2: inlet pressure of the stator impeller 12 P3: outlet pressure of the stator impeller 12 27, the bosses 11a, 1a of the turbine impeller 11 and the stator
The gap g2 between 2a and 2a is sufficiently narrowed, and the gap g1 between the pump impeller 10 and the stator impeller 12 is expanded to form the oil inlet 30, so that the entire amount of oil discharged by the oil pump 27 is reduced to the oil inlet. 30 to the outlet of the stator impeller 12, and the outlet pressure P3
Therefore, the generation of bubbles in the oil at the exit of the stator impeller 12 can be prevented as much as possible, and the reduction of the torque ratio and the transmission efficiency due to the generation of bubbles can be prevented.

Since the gap g2 between the bosses 11a and 12a of the turbine impeller 11 and the stator impeller 12 is sufficiently narrowed, the oil that has exited the turbine impeller 11 is removed from the boss of the stator impeller 12 through the gap g2. 12a can be prevented from flowing to the inner peripheral side of the turbine impeller 11a.
Of the oil that has passed through the stator impeller 12, it is possible to prevent a decrease in torque ratio and transmission efficiency due to oil flowing out to the gap g2.

FIG. 6 is a diagram showing the relationship between the position of the oil inlet 30 and the torque ratio obtained by the test. In the figure, denotes the oil inlet 30 and the boss 1 of the stator impeller 12.
When the oil inlet 30 is provided only in the gap g2 on the turbine impeller 11 side of the boss 12a of the stator impeller 12, when the gaps g1 and g2 are provided on both sides of the 2a (the present invention).
Shows a case where the oil inlet 30 is provided only in the gap g1 on the pump impeller 10 side of the boss 12a of the stator impeller 12.
As can be seen from the figure, when the discharge pressure of the oil pump 27 was relatively high, no change was observed in the torque ratio at and. However, as the discharge pressure decreased, the torque ratio at and decreased. In contrast, (the present invention)
The torque ratio at did not decrease.

When the torque amplifying operation is completed, the stator impeller 12 rotates in the same direction together with the pump impeller 50 and the turbine impeller 51 while idling the freewheel 18 due to the reversal of the torque direction applied thereto.

Next, in the second embodiment of the present invention shown in FIG. 3, an annular seal member 39 is interposed between the bosses 11a and 12a of the turbine impeller 11 and the stator impeller 12. Other configurations are the same as those of the previous embodiment.
In FIG. 3, portions corresponding to those of the previous embodiment are denoted by the same reference numerals, and description thereof will be omitted.

According to the second embodiment, the gap g2 between the bosses 11a and 12a of the turbine impeller 11 and the stator impeller 12 is sealed by the seal member 39.
Outflow and inflow of oil through the gap g2 can be reliably prevented. Therefore, the oil pump 27
Can be supplied from the oil inlet 30 to the outlet of the stator impeller 12, the oil flowing out of the turbine impeller 11 can be prevented from flowing out to the gap g2, and the torque ratio and the outlet efficiency can be reduced. Reduction can be effectively prevented.

In the third embodiment of the present invention shown in FIG.
The axial position of the boss 12a of the stator impeller 12 is determined by the bosses 10a, 11 of the pump impeller 10 and the turbine impeller 11.
a each boss 10a, 11a, 12a
The gaps g1 and g2 between them are set as small as possible. A plurality of radial grooves communicating the cutouts 40 of the boss 12a with the outlet of the stator impeller 12 are provided on one or both of the opposing surfaces of the bosses 10a, 12a of the pump impeller 10 and the stator impeller 12 as the oil inlet 30. 45 and 46 are provided.

In this case, the boss 11 of the turbine impeller 11
It is preferable to reduce the gap between the outer peripheral surface of a and the stator impeller 12 as much as possible or to interpose an annular seal member 48 between the opposed surfaces. Since the other configuration is the same as that of the first embodiment, the same reference numerals in FIG. 4 denote the same parts as in the first embodiment, and a description thereof will be omitted.

According to the third embodiment, the same operation and effect as those of the first and second embodiments can be achieved.
The gaps g1, g2 between the bosses 10a, 11a, 12a can be sufficiently reduced to minimize the axial movement of the stator impeller 12.

In the fourth embodiment of the present invention shown in FIG. 5, the boss 12a of the stator impeller 12 is used as the oil inlet 30.
The structure is the same as that of the third embodiment shown in FIG. 4 except that a through hole 47 for communicating with the outlet of the stator impeller 12 is provided in the boss 10 a of the pump impeller 10. The same reference numerals are given to the portions corresponding to the examples, and the description thereof will be omitted.

According to the fourth embodiment, the same functions and effects as those of the third embodiment can be achieved.

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.

[0046]

As described above, according to the first feature of the present invention, both bosses of the pump impeller and the turbine impeller are opposed to both sides of the boss of the stator impeller. In a torque converter having an oil outlet provided in an inner peripheral side of a supply oil passage communicating with an oil pump and an oil chamber formed on the back side of the turbine impeller and communicating between the pump impeller and the turbine impeller, And the gap between the bosses of the stator impeller is substantially closed, and at least one of the bosses of the pump impeller and the stator impeller is
An oil inlet is provided to connect the inner periphery of the boss of the stator impeller to the exit of the stator impeller. Therefore, when a large pressure difference is generated between the entrance and the exit of the stator impeller, the discharge pressure of the oil pump is remarkable. Even if it drops, the entire amount of oil discharged from the oil pump will be supplied from the oil inlet to the outlet of the stator impeller, effectively suppressing the drop in the outlet pressure and preventing the generation of bubbles in the oil. Oil flowing out of the turbine impeller is prevented from flowing out between the bosses of the turbine impeller and the stator impeller, thereby effectively suppressing a decrease in torque ratio and transmission efficiency.

According to a second feature of the present invention, the oil inlet is provided between the pump impeller and the stator impeller boss which is larger than the narrowed gap between the turbine impeller and the stator impeller boss. Since the gap is formed, the torque ratio and the transmission efficiency can be prevented from lowering with a simple structure.

According to the third aspect of the present invention, the oil inlet is formed by a radial groove formed on at least one of the opposing surfaces of the bosses of the pump impeller and the stator impeller. , And a reduction in torque ratio and transmission efficiency can be prevented.

According to a fourth feature of the present invention,
Since the oil inlet is constituted by a through-hole formed in the boss of the pump impeller, the structure can be simplified,
The reduction of the torque ratio and the transmission efficiency can be prevented.

According to a fifth feature of the present invention,
Since an annular sealing member is interposed between the opposing surfaces of the boss of the turbine impeller and the stator impeller, the gap between the boss of the turbine impeller and the boss of the stator impeller is sealed by the sealing member, and the oil passing through the gap is sealed. Can be reliably prevented from flowing in and out, and can further contribute to preventing a decrease in torque ratio and transmission efficiency.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a torque converter showing a first embodiment of the present invention.

FIG. 2 is an enlarged view of a part of FIG.

FIG. 3 is an enlarged view corresponding to FIG. 2, showing a second embodiment of the present invention.

FIG. 4 is an enlarged view showing a third embodiment of the present invention and corresponding to FIG. 2;

FIG. 5 is an enlarged view showing a fourth embodiment of the present invention and corresponding to FIG. 2;

FIG. 6 is a characteristic diagram of the torque converter of the present invention.

[Explanation of symbols]

T: torque converter g1: gap between bosses of pump impeller and stator impeller g2: gap between bosses of turbine impeller and stator impeller 10: pump impeller 11 Turbine impeller 12 Stator impeller 25 Supply oil path 27 Oil pump 30 Oil inlet 31 Oil outlet 39 Seal member 41 ... Oil chamber 45, 46 ... Radial groove as oil inlet 47 ... Through hole as oil inlet 48 ... Seal member

Claims (5)

[Claims] 1. A boss (12) of a stator impeller (12).
a), both bosses (10a, 11a) of a pump impeller (10) and a turbine impeller (11) are opposed to each other, and an oil pump is provided on the inner peripheral side of the boss (12a) of the stator impeller (12). An oil chamber (41) communicating with a supply oil passage (25a) connected to (27), formed on the back side of the turbine impeller (11), and communicating between the pump impeller (10) and the turbine impeller (11). In the torque converter provided with the oil outlet (31), the gap (g2) between the bosses (11a, 12a) of the turbine impeller (11) and the stator impeller (12) is substantially closed, and the pump impeller ( At least one of the boss (10a, 12a) of the stator impeller (12) and the boss (12) of the stator impeller (12).
A torque converter, characterized in that an oil inlet (30) communicating the inner peripheral side of (a) to the outlet of the stator impeller (12) is provided. 2. The torque converter according to claim 1, wherein the oil inlet is connected to a turbine impeller.
1) and the bosses (11a, 12) of the stator impeller (12).
a) The boss (10) of the pump impeller (10) and the stator impeller (12), which is larger than the narrowed gap (g2) between them.
a, a torque converter comprising a gap (g1) between the torque converters. 3. The torque converter according to claim 1, wherein said oil inlet is connected to a pump impeller.
And bosses (10a, 12a) of the stator impeller (12)
Radial grooves (4) formed on at least one of the opposing surfaces of
5, a torque converter characterized by comprising: 4. The torque converter according to claim 1, wherein said oil inlet is connected to a pump impeller.
A torque converter characterized by comprising a through hole (47) formed in the boss (10a). 5. The torque converter according to claim 1, wherein the boss (1) of the turbine impeller (11) is provided.
A torque converter, comprising an annular seal member (39, 48) interposed between opposing surfaces of 1a) and a stator impeller (12).