JPH0996349A - Impeller for torque converter - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance fuel consumption at the time of idling, and restrain simultaneously the occurrence of creeping while a transmission efficiency and a torque ratio are being maintained. SOLUTION: This impeller for a torque converter which is so constituted that, in the impeller for a torque converter where a stator impeller 3 is interposed between a turbine impeller and a pump impeller, the stator impeller 3 is divided into a front vane impeller 34 and a rear vane impeller 35, when it is detected that the stator impeller is idling, the front vane impeller 34 and the rear vane impeller 35 are slid in the circumferential direction, and positional relation of them is changed, so that a circulation passage area can thereby be controlled.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention divides a stator impeller constituting a torque converter into a front blade impeller and a rear blade impeller, and, in an idling state, the front impeller impeller By changing the circumferential positional relationship with the rear impeller and controlling the circulating flow passage area, the circulating flow is controlled and the capacity coefficient is controlled to maintain the transmission efficiency and the torque ratio. However, the present invention relates to a torque converter impeller that improves fuel efficiency and suppresses creep when idling.

[0002]

2. Description of the Related Art A conventional impeller for a torque converter (Japanese Patent Laid-Open No. 57-69162) has a pump P as shown in FIG.
When the rotational speed of the turbine T is low, a fluid flow that occurs inside the core, that is, a flow that passes through the back portion of the movable rotor blade M of the stator S, receives the flow of the movable stator rotor blade M in a direction that reduces the angle thereof. The rotary blade M is swung.

At the time of stall in which the turbine is stopped even though the pump is rotating at a low speed, the pressing force of the spring B causes the movable stator rotor blades M to swing around the axis J, increasing the angle, and It obstructed the flow, reduced the torque capacity, and reduced the load on the engine.

[0004]

In the conventional impeller for a torque converter described above, it is necessary to add new parts to the pump P and the turbine T as well as the stator S, so that the rotational inertia changes, and There was a problem that the structure became complicated.

Therefore, the present inventors divided the stator impeller constituting the torque converter into a front blade impeller and a rear blade impeller, and, in an idling state, the front blade impeller and the front blade impeller. Focusing on the technical idea of the present invention that the positional relationship in the circumferential direction with the rear blade impeller is changed to control the circulation passage area to control the circulation flow to control the capacity coefficient, and Through repeated research and development, the present invention has been achieved which achieves the object of improving fuel efficiency and suppressing creep during idling while maintaining transmission efficiency and torque ratio.

[0006]

The torque converter impeller of the present invention (the first invention according to claim 1) is a torque in which a stator impeller is arranged between a pump impeller and a turbine impeller. In the converter impeller, the stator impeller is divided into a front blade impeller and a rear blade impeller, and, in an idling state, a circumference of the front blade impeller and the rear blade impeller is divided. The configuration is such that the positional relationship in the direction can be changed to control the circulation flow passage area.

In the torque converter impeller of the present invention (the second invention according to claim 2), in the first invention, the front blade impeller and the rear blade impeller are the outer rings of a one-way clutch. It is configured to be slidable in the circumferential direction along a groove formed on the outer peripheral surface.

The impeller for a torque converter according to the present invention (the third invention according to claim 3) is the impeller for a torque converter according to the second invention, in the idling state due to a change in torque acting on the stator impeller. The impeller is configured to slide in the negative pressure surface direction.

The impeller for a torque converter of the present invention (the fourth invention according to claim 4) is the impeller for a torque converter according to the third invention, wherein the impeller is provided between the inner side of the front blade impeller and the outer ring of the one-way clutch. A spring for biasing the blade impeller toward the positive pressure surface in the circumferential direction is inserted, and the rear blade impeller is circumferentially positively arranged between the inner side of the rear blade impeller and the outer ring of the one-way clutch. A first spring that biases the pressure surface side is inserted, and
A second spring is inserted to urge the rear blade impeller so as to engage with the outer ring of the one-way clutch at a certain torque or less.

(Operation) In the torque converter impeller of the first invention having the above-described structure, the stator impeller disposed between the pump impeller and the turbine impeller is the front blade impeller and the front impeller. In the idling state, it is divided into a rear blade impeller, and in the idling state, the positional relationship in the circumferential direction between the front blade impeller and the rear blade impeller is changed to control the circulation flow passage area and To control the capacity coefficient.

In the torque converter impeller of the second aspect of the present invention, the stator impeller disposed between the pump impeller and the turbine impeller has the front blade impeller and the rear blade impeller. In the idling state, the front blade impeller and the rear blade impeller are circumferentially slid along the groove formed on the outer peripheral surface of the outer ring of the one-way clutch in an idling state. Then, the area of the circulation passage is controlled, and the circulation coefficient is controlled to control the capacity coefficient.

In the torque converter impeller of the third aspect of the present invention, the stator impeller disposed between the pump impeller and the turbine impeller has the front blade impeller and the rear blade impeller. In the idling state, the front blade impeller is divided into an impeller and a negative groove along the groove formed on the outer peripheral surface of the outer ring of the one-way clutch. The area of the circulation passage is controlled by sliding in the circumferential direction toward the pressure surface side, and the circulation coefficient is controlled to control the capacity coefficient.

In the torque converter impeller of the fourth aspect of the present invention, the stator impeller disposed between the pump impeller and the turbine impeller has the front blade impeller and the rear blade impeller. The front blade impeller, which is divided into an impeller and is inserted between the inner side of the front blade impeller and the outer ring of the one-way clutch by torque acting on the stator impeller in an idling state. The front impeller is slid in the circumferential direction toward the suction surface along the groove formed on the outer peripheral surface of the outer ring of the one-way clutch against the spring that urges the front surface in the circumferential positive pressure surface side. It On the other hand,
The front wing portion is resisted against a first spring that urges the rear blade impeller, which is interposed between the inside of the rear blade impeller and the outer ring of the one-way clutch, toward the positive pressure surface side in the circumferential direction. The impeller is slid in the circumferential direction along the groove formed on the outer peripheral surface of the outer ring of the one-way clutch toward the negative pressure surface side, but by the biasing force of the inserted second spring. ,
When the torque is equal to or less than a certain torque, the rear blade impeller is locked to the outer ring of the one-way clutch, so that the rear blade impeller does not slide in the circumferential direction toward the suction surface side. Therefore, since only the front blade impeller is slid in the circumferential direction toward the suction surface side, the circulation passage area is controlled, the circulation flow is controlled, and the capacity coefficient is controlled.

[0014]

In the torque converter impeller according to the first aspect of the present invention, the positional relationship in the circumferential direction between the front impeller and the rear impeller changes in the idling state. Since the circulation passage area is controlled, the circulation flow is controlled, and the capacity coefficient is controlled, there is an effect that fuel efficiency is improved and creep is suppressed during idling while maintaining the transmission efficiency and the torque ratio.

In the torque converter impeller of the second aspect of the present invention, in the idling state, the divided front blade impeller and rear blade impeller are located on the outer peripheral surface of the outer ring of the one-way clutch. Since the circulation flow passage area is controlled by sliding the groove in the circumferential direction along the groove formed in, the structure is simple and the rotational inertia does not change.

In the torque converter impeller of the third invention having the above-described operation, the idling state is detected by the change of the torque acting on the stator impeller, and the front blade impeller is automatically slid to circulate. This has the effect of controlling the flow passage area.

In the impeller for a torque converter according to the fourth aspect of the present invention, the rear impeller is forcibly applied to the outer ring of the one-way clutch in an idling state below a certain torque by the urging force of the second spring. And the front impeller is slid in the circumferential direction toward the suction surface to control the area of the circulation flow passage and control the circulation flow to realize the control of the capacity coefficient. .

[0018]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) In a torque converter impeller of a first embodiment, a stator impeller 3 is disposed between a turbine impeller 1 and a pump impeller 2 as shown in FIGS. 1 to 7. In the impeller for a torque converter, the stator impeller 3 is divided into a front blade impeller 34 and a rear blade impeller 35, and when the idling state is detected, the front impeller 34 is The rear blade impeller 35 is configured to slide in the circumferential direction to change the positional relationship and control the circulation passage area.

As shown in FIG. 2, the torque converter is integrally formed with a pump impeller 2 which is rotationally driven by an engine (not shown) and a transmission input shaft 10 and is coaxially rotatable. The turbine impeller 1 and the stator impeller 3 which is connected to the stator shaft 11 fixed to the transmission case via the one-way clutch 31 and is arranged between the turbine impeller 1 and the pump impeller 2. Become.

As shown in FIGS. 1, 3 and 4, the stator impeller 3 has an inner ring 32 corresponding to a shell and an outer ring 33 corresponding to a core arranged coaxially with the inner ring 32.
And a large number of stator blades 4 arranged in the radial direction between the inner ring 32 and the outer ring 33, and are formed by die casting using aluminum alloy or the like.

As shown in FIG. 3, the stator blades 4 are in the form of thick blades as a whole, and are composed of a positive pressure surface 42 which is a concave surface and a negative pressure surface 43 which is a convex surface. Is divided into a front edge portion 44 that constitutes the rear blade portion impeller 35 and a rear edge portion 45 that constitutes the rear blade impeller 35 corresponding to the front and rear of the flow.

The front vane impeller 34 and the rear vane impeller 35, which are the axially divided front and rear parts of the stator impeller 3, are the outer ring 3 of the one-way clutch 31.
It is configured such that it can relatively slide in the circumferential direction along the grooves 311 and 312 formed on the outer peripheral surface of 10.

The stator impeller 3 slides the front blade impeller 34 in the direction of the suction surface 43 (upward in FIG. 3) in an idling state due to a change in torque acting as shown in FIG. It consists of the configuration to obtain.

That is, in the front blade impeller 34 of the stator impeller 3, as shown in FIG. 4 and FIG. 5, there is a circumferential direction between the inside of the inner ring 32 and the outer ring 310 of the one-way clutch 31. A plurality of coil springs 36 for biasing the front blade impeller 34 toward the positive pressure surface in the circumferential direction are inserted in the formed circumferential groove 311. By a torque acting on the stator impeller 3 in an idling state. The front blade impeller 34 is resisted against the biasing force of the coil spring 36.
Can be slid toward the negative pressure surface side in the circumferential direction.

As shown in FIG. 6, in the trailing blade impeller 35, the inner circumferential surface of the inner race 32 and the outer race 310 of the one-way clutch 31 are circumferentially formed in the circumferential groove 312. , A plurality of first coil springs 37 for urging the rear blade impeller 35 toward the positive pressure surface in the circumferential direction are inserted, and the rear blade impeller 35 is moved to the one-way clutch 31 at a certain torque or less. The outer ring 31
A plurality of second springs 38 that are biased so as to be locked at 0 are inserted in a radial groove 351 formed in the radial direction.

That is, as shown in FIG. 7, the second spring 38 has the plunger 3 inserted in the radial groove 351 formed in the boss portion of the rear blade impeller 35 in the radial direction.
A ball plunger 35 which is inserted in 52, has a ball 353 disposed at its tip, and engages with a conical groove 313 formed in the outer ring 310 of the one-way clutch 31.
2 is configured, and when the torque acting on the stator impeller 3 is equal to or less than a certain value as in the idling state, the locked state of the rear blade impeller 35 to the one-way clutch 31 is maintained.

In the torque converter impeller of the first embodiment having the above structure, when the torque converter starts operating, the turbine impeller 1 to the stator impeller 3 are operated.
The working fluid that has flowed in flows along the wall surface of the stator blade 4 to change its flow direction and flow into the pump 2.

In the idling state, due to the torque acting on the stator impeller 3, the inside of the front blade impeller 34 and the outer ring 3 of the one-way clutch 31.
10 against the coil spring 36 that biases the front blade impeller 34 interposed between the front blade impeller 34 and the coil spring 36 toward the positive pressure surface in the circumferential direction. The circumferential groove 311 formed on the outer peripheral surface of the outer ring 310.
9A, it is slid toward the negative pressure surface side in the circumferential direction as shown in FIG. 9 (A).

On the other hand, the rear blade impeller 35 interposed between the inner side of the rear blade impeller 35 and the outer ring 310 of the one-way clutch 31 is urged toward the positive pressure surface side in the circumferential direction. The rear impeller 35 against the coil spring 37 of No. 1
Is slid to the circumferential negative pressure surface side along the circumferential groove 312 formed on the outer circumferential surface of the outer ring 310 of the one-way clutch 31, but the ball plunger inserted in the radial direction. The second constituting 352
Due to the urging force of the coil spring 38, the rear blade impeller 3 is operated under a certain torque such as an idling state.
Since 5 is locked in the conical groove 313 formed in the outer ring 310 of the one-way clutch 31, the rear blade impeller 35 does not slide to the suction surface side in the circumferential direction.

Therefore, as shown in FIG. 9 (A), only the front blade impeller 34 is slid in the circumferential direction toward the negative pressure surface side, so that the effective area of the circulation channel is mechanically reduced,
The capacity coefficient is controlled by reducing the circulating flow as shown in FIG.

When the vehicle starts from the idling state, the number of revolutions of the pump impeller 2 increases, the speed ratio increases and the circulation flow rate increases, and the rear blade impeller 3 increases.
5, the torque acting on 5 increases and exceeds the constant torque determined by the biasing force of the second coil spring 38 forming the ball plunger 352 (about 700).
rpm), the rear blade impeller 35 slides to the suction surface side, and the rear blade impeller 35 and the front blade impeller 34 are combined as shown in FIG. 9B in the converter area. Then it becomes a normal wing shape.

In the subsequent acceleration state, the torque decreases as the speed ratio increases (FIG. 9 (B)), but in the converter region, the direction of the torque acting on the leading edge portion 44 and the trailing edge portion 45 of the stator blade 4 is As it does not change, Fig. 9 (B)
Is maintained.

During steady running of the vehicle, when the speed ratio becomes large and exceeds the coupling point, the stator impeller 3 idles due to the action of the one-way clutch 31. Since the torque of is slightly applied, the front impeller 3
4 and the rear blade impeller 35 become unstable in position, but the front blade portion 41 and the rear blade portion 42 apply a biasing force to the one-way clutch 31 in the same direction as the direction of the torque. Coil spring 36 and first coil spring 37
Causes the front wing part 41 and the rear wing part 42 to be united to the initial position, and the normal wing shape is maintained as shown in FIG. 9C in the coupling region.

In the torque converter impeller of the first embodiment having the above-described operation, the positional relationship in the circumferential direction between the front blade impeller 34 and the rear blade impeller 35 changes in the idling state. As a result, the area of the circulation flow path is reduced, the circulation flow is controlled, and the capacity coefficient is controlled as shown by the solid line in FIG. 12, so that the effect of improving fuel consumption and suppressing creep can be achieved.

That is, the impeller for a torque converter of the first embodiment maintains the conventional characteristics in transmission efficiency, torque ratio and capacity coefficient as shown in FIGS. 14 to 16 based on a constant speed test of 1500 rpm. After doing
The effects described above are realized. In particular, the high speed ratio efficiency, torque ratio, and capacity coefficient are unchanged.

Further, in the torque converter impeller of the first embodiment, in the idling state, the divided front blade impeller 34 and the divided rear blade impeller 35 are shown in FIG.
As shown in (A), the circumferential groove 311 formed on the outer peripheral surface of the outer ring 310 of the one-way clutch 31,
Since the circulation flow passage area is controlled by sliding it in the circumferential direction along the 312, the structure is simple and the rotational inertia does not change.

Further, in the torque converter impeller of the first embodiment, the idling state is detected by the decrease in the torque acting on the stator blades 4 of the stator impeller 3, and the front blade impeller 34 is automatically operated. It is possible to reduce the area of the circulation flow path by sliding it to the position.

Further, in the torque converter impeller of the first embodiment, in the idling state in which the torque acting on the stator blade 4 by the urging force of the second coil spring 38 is equal to or less than a certain value, the rear blade impeller 35 is used. Is forcibly locked to the outer ring 310 of the one-way clutch 3 and only the front blade impeller 34 is slid in the circumferential direction toward the suction surface side to reduce the circulation flow passage area and the circulation flow. As a result, it is possible to reduce the capacity coefficient by 40% at the maximum as shown in FIG.

Further, the impeller for a torque converter according to the first embodiment has an effect that energy supply from the outside is not required and that a new sensor and an actuator are not required to be added, and the above effect is achieved without increasing the cost. Has the effect of realizing.

In the torque converter impeller of the first embodiment, the stator impeller 3 is replaced by the front blade impeller 34.
Also, since the new blade and the rear blade impeller 35 are simply divided and the new components and parts protruding to the existing components and parts are not added, the rotational inertia does not change and the structure becomes complicated. There is no effect.

Further, in the torque converter impeller of the first embodiment, the circumferential coil springs 36, 37 and the circumferential coil springs 36, 37 for controlling the movement of the divided front blade impeller 34 and rear blade impeller 35 are provided. Even when the radial coil spring 38 does not operate, the function as a conventional integral type stator is realized, so that an effect of realizing fail-safe is achieved.

Further, in the torque converter impeller of the first embodiment, the change in the capacity coefficient at the time of stop is set to 600 rpm for the pump speed in order to simulate the state at the time of deceleration and stop.
At m (the accelerator is not stepped on), if the turbine rotational speed is lowered from a state higher than the pump rotational speed to 0, the state shown in FIG. 9 (C) changes to the state shown in FIG. 9 (A). As shown in 13, it becomes clear that the capacity coefficient can be reduced when the engine is stalled again.

(Second Embodiment) In a torque converter impeller of a second embodiment, as shown in FIGS. 17 to 19, the stator impeller 3 is divided into a front blade impeller 34 and a rear blade impeller 35. This is different from the first embodiment in that the divided surface 46 is formed so as to be inclined with respect to the circumferential direction perpendicular to the axis, and the same portions are denoted by the same reference numerals and description thereof is omitted.

In the idling state, the front blade impeller 34 is formed on the outer peripheral surface of the outer ring 310 of the one-way clutch 31 by the torque acting on the stator blades 4 of the stator impeller 3. Since it slides in the circumferential direction along the circumferential groove 311 toward the negative pressure surface 43 side as shown in FIG. 18, it is between the facing divided surfaces 46 of the front blade impeller 34 and the rear blade impeller 35. A gap is formed to form a conduction path 47 that electrically connects the positive pressure surface 42 and the negative pressure surface 43.

In the torque converter impeller of the second embodiment having the above-mentioned configuration, in the idling state, the divided front blade impeller 34 has the circumferential negative pressure surface 43.
By sliding to the side (upper side in FIG. 17), the effective area of the circulation channel is mechanically reduced, the circulation flow is reduced, and the capacity coefficient is controlled.

Further, in the second embodiment, the front blade impeller 34 slides toward the suction side in the circumferential direction, so that the front blade impeller 34 and the rear blade impeller 35.
Since a gap is formed between the divided surfaces 46 facing each other to form the conduction path 47 that electrically connects the positive pressure surface 42 and the negative pressure surface 43, a part of the working fluid flowing into the stator impeller 3 is formed. From the positive pressure surface 42 through the conduction path to the negative pressure surface 43 side in a direction counter to the flow along the stator blades 4.

Therefore, the fluid led out to the negative pressure surface 43 side by the conduction path 47 flows into the front edge portion of the separation region formed on the negative pressure surface 43 side in the direction opposite to the flow along the stator blades 4. Therefore, the separation region grows and becomes large, and the effective flow passage cross-sectional area between the stator blades 4 is reduced, so that the circulation flow rate is reduced.

In the torque converter impeller of the second embodiment having the above-described operation, in the idling state, the front blade impeller 34 has the circumferential negative pressure surface 43 side (FIG. 17).
By sliding inward (upper middle), the effective area of the circulation channel is mechanically reduced, the circulation flow is reduced, and the capacity coefficient is controlled, so that there is an effect that fuel efficiency is improved and creep is suppressed.

In the impeller for a torque converter according to the second embodiment, the front blade impeller 34 slides toward the negative pressure surface in the circumferential direction, so that a gap is formed between the divided surfaces 46 and the positive pressure surface. 42 forms the conduction path 47 that electrically connects the negative pressure surface 43 to the negative pressure surface 43. Therefore, a part of the working fluid flowing into the stator impeller 3 passes through the conduction path from the positive pressure surface 42 and the negative pressure surface 43. Since it is introduced and discharged to the side in the direction opposite to the flow along the stator blades 4, there is an effect that the capacity coefficient characteristic is controlled by controlling the circulation flow rate of the torque converter.

In the torque converter impeller of the second embodiment, the stator impeller 3 is replaced by the front blade impeller 34.
By dividing into the rear vane impeller 35 and forming the conducting path 52 in the stator vane 4, it is not necessary to add an attaching ring as in the conventional device. To prevent the increase of
This has the effect of preventing an increase in cost.

The embodiments described above are merely examples for the purpose of explanation, and the present invention is not limited to them. Those skilled in the art will recognize from the claims, the detailed description of the invention and the description of the drawings. Modifications and additions can be made without departing from the technical idea of the present invention.

In the above-described second embodiment, as an example, as shown in FIG. 17, an example was described in which the outlet on the suction surface side of the above-mentioned passage is formed substantially at right angles to the blade surface of the suction surface. The present invention is not limited to this, and a smaller angle than a right angle having a flow component along the suction surface to some extent can be adopted as long as it is within a direction and a range that promotes separation of the suction surface, even if it is a large angle. is there.

In the above-described embodiment, the example of the linear divided surface of the stator impeller has been described as an example, but the present invention is not limited to this, and an arc-shaped divided surface and a conduction path are adopted. It is possible.

[Brief description of drawings]

FIG. 1 is a sectional view showing a stator impeller of a first embodiment of the present invention.

FIG. 2 is a vertical cross-sectional view showing the entire torque converter of the first embodiment.

FIG. 3 is a partial cross-sectional view showing a stator blade of the first embodiment.

FIG. 4 is a front view showing an impeller of a stator according to the first embodiment.

FIG. 5 is a partial enlarged cross-sectional view showing a front blade impeller and a one-way clutch of the first embodiment.

FIG. 6 is a partially enlarged cross-sectional view showing a trailing blade impeller and a one-way clutch of the first embodiment.

FIG. 7 is a cross-sectional view showing the ball plunger of the first embodiment.

FIG. 8 is a diagram showing a relationship between a speed ratio and a stator torque in the first embodiment.

FIG. 9 is an explanatory diagram for explaining a positional relationship between the front wing portion and the rear wing portion in the converter region and the coupling region during idling in the first embodiment.

FIG. 10 is a diagram showing a relationship between a sliding amount and a drawing ratio of a front wing portion and a stall capacity coefficient according to the first embodiment.

FIG. 11 is an explanatory diagram for explaining the definition of the aperture ratio in the first embodiment.

FIG. 12 is a diagram showing a relationship between a pump rotation speed and a stall capacity coefficient in the first embodiment.

FIG. 13 is a pump rotation speed of 600 rpm according to the first embodiment.
4 is a diagram showing the relationship between turbine rotational speed and capacity coefficient in FIG.

FIG. 14 is a diagram showing a relationship between a speed ratio and efficiency in the first embodiment.

FIG. 15 is a diagram showing a relationship between a speed ratio and a torque ratio in the first embodiment.

FIG. 16 is a diagram showing a relationship between a speed ratio and a capacity coefficient in the first embodiment.

FIG. 17 is a partial cross-sectional view showing a stator blade of the second embodiment of the present invention.

FIG. 18 is a partial cross-sectional view showing a state in which the front blade portion of the stator blade of the second embodiment moves toward the negative pressure surface side in the circumferential direction and a conduction portion is formed between the divided surfaces.

FIG. 19 is a sectional view showing a stator impeller of the second embodiment.

FIG. 20 is a partial cross-sectional view showing a movable stator blade in a conventional torque converter.

[Explanation of symbols]

 1 Turbine Impeller 2 Pump Impeller 3 Stator Impeller 34 Front Blade Impeller 35 Rear Blade Impeller

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Satoru Matsushima Aichi Prefecture, Nagakute-cho, Aichi-gun, Nagazai 1-41, Yokomichi Toyota Central Research Institute Co., Ltd. (72) Inventor Masahiro Kojima 1-Toyota-cho, Toyota-shi, Aichi Inside Toyota Motor Corporation

Claims (4)

[Claims] 1. A torque converter impeller in which a stator impeller is arranged between a pump impeller and a turbine impeller, wherein the stator impeller is a front blade impeller and a rear blade impeller. In the idling state, the torque is characterized in that the circulation passage area can be controlled by changing the circumferential positional relationship between the front blade impeller and the rear blade impeller in a divided state. Impeller for converter. 2. The front impeller and the rear impeller according to claim 1, wherein the front impeller and the rear impeller are configured to be slidable in a circumferential direction along a groove formed on an outer peripheral surface of an outer ring of a one-way clutch. An impeller for a torque converter, which is characterized in that 3. The torque converter according to claim 2, wherein in a idling state due to a change in torque acting on the stator impeller, the front vane impeller is slid in a suction surface direction. Impeller. 4. The spring according to claim 3, wherein a spring that urges the front blade impeller toward the positive pressure surface in the circumferential direction is interposed between the inside of the front blade impeller and the outer ring of the one-way clutch, A first spring for urging the rear blade impeller toward the positive pressure surface in the circumferential direction is interposed between the inner side of the rear blade impeller and the outer ring of the one-way clutch, and at a certain torque or less, An impeller for a torque converter, wherein a second spring that urges the rear blade impeller to engage with the outer ring of the one-way clutch is inserted.