JP2009014114A - Torque converter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure a torque capacity in a range of a speed ratio from a low-speed ratio zone to a medium-speed ratio zone even if the torque capacity at a stall is reduced. <P>SOLUTION: A stator 1 is constituted in such a manner that second stator blades 1B each having a cut face 1g which is vertical to a rotation axis R formed by notching a region from a negative pressure face 1d including a front edge in a basic blade form of the stator blade toward a pressurizing face 1c are arranged every equal number of sheets with respect to stator blades 1A of basic blade types. The torque capacity at the stall is reduced by adjusting a ratio of the second stator blades 1B to the first stator blades 1A, and thereby the torque capacity in the range from the low-speed rate zone to the middle-speed rate zone can be secured. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a structure of a torque converter used for a drive system of a vehicle.

  As is well known, the torque converter is composed of three impellers: a pump impeller filled with oil, a turbine runner, and a stator. The pump impeller is connected to the input shaft to convert the rotational force from the engine into an oil flow, and the turbine runner connected to the output shaft receives this oil flow and converts it into torque. During this time, the stator exerts an effect of increasing the transmission torque by changing the flow direction of the oil coming out of the turbine runner.

FIG. 12 is a view showing a stator blade of a torque converter according to a conventional example.
In a conventional torque converter stator, a plurality of stator blades 50 having a basic blade shape are arranged around the rotation axis R, and hydraulic oil for operating the torque converter is supplied from a turbine runner (not shown) located on the left side in the drawing. After that, it moves between the stator blades 50 and moves toward a pump impeller (not shown) located on the right side in the drawing.
Here, the end of the stator blade 50 on the turbine runner side is referred to as a front edge 52, and the end of the pump impeller side is referred to as a rear edge 53, and the front edge 52 and the rear edge 53 are connected to face the pump impeller side. Is a negative pressure surface 54, and a surface connecting the front edge 52 and the rear edge 53 and facing the turbine runner side is referred to as a positive pressure surface 55.
The flow direction of the working oil that flows into the stator and toward the stator blades 50 changes according to the speed ratio. When the flow direction of the working oil is perpendicular to the chord 51 of the stator blade 50, the working oil flows so as to go around the front edge 52 of the stator blade and then moves toward the trailing edge 53 side. At that time, separation occurs on the negative pressure surface 54 side of the stator blade 50, and as a result of the decrease in the cross-sectional area of the flow path between adjacent stator blades due to the separation, the torque capacity decreases.

Therefore, each stator blade 50 is arranged in a direction in which the fluid loss in the high speed ratio region is minimized so that the occurrence of separation in the high speed ratio region is suppressed. In the stator having such stator vanes 50, the speed ratio, the low speed ratio range, through the medium speed ratio range, according to reach the speed ratio range, the flow direction of the working oil from the direction indicated by arrow F _L , Arrow F _M and arrow F _H.

  The performance of the torque converter is as follows: speed ratio e (= output shaft rotational speed / input shaft rotational speed), torque ratio t (= output shaft torque / input shaft torque), and torque capacity T (= input shaft rotational speed). Torque).

If the torque capacity (stall torque capacity) at the time of stall (speed ratio = 0) in which the rotation of the engine is not transmitted to the transmission side is large, the load on the engine increases, and the idle fuel consumption deteriorates.
Therefore, in order to reduce the stall torque capacity and improve the idle fuel consumption, a flat portion parallel to the line segment (blade chord) connecting the leading edge and the trailing edge of the stator blade is formed on the pressure surface of the stator blade. This is disclosed in Patent Document 1.
Japanese Patent Laid-Open No. 08-021508

  However, in the case of the invention described in Patent Document 1, the torque capacity at the time of stall can be reduced, but the torque capacity in the range from the low speed ratio range to the medium speed ratio range other than at the time of stall is temporarily reduced. It cannot be raised. Therefore, the torque capacity in such a range tends to decrease, and it is difficult to set the torque capacity according to the engine output on the vehicle side.

  Therefore, the present invention secures the torque capacity in such a range when the speed ratio shifts from the low speed ratio area to the medium speed ratio area even when the torque capacity at the time of stall is reduced, An object of the present invention is to provide a torque converter capable of setting a torque capacity according to an engine output on the vehicle side.

  The present invention relates to a torque converter including a pump impeller and a turbine runner that rotate around a common rotating shaft, and a stator interposed in an oil flow passage from the turbine runner to the pump impeller. The cut surface perpendicular to the rotation axis formed by cutting out the region including the front edge in the mold, or the front edge side end of the pressure surface is downstream in the oil flow direction from the front edge side end of the suction surface In this way, the stator blades having the inclined cut surfaces are arranged at equal intervals with respect to the basic blade type stator blades.

According to the present invention, in the stator blade in which the region including the leading edge in the basic airfoil is cut out to form a cut surface, the flow of the working oil when the speed ratio is in the range from the low speed ratio range to the medium speed ratio range. Since the cut surface faces in the direction, the stator blade formed with the cut surface will cause greater separation from the low speed ratio region to the medium speed ratio region than the stator blade not formed with the cut surface. . Therefore, the stator blade having the cut surface is separated more greatly than the stator blade having no cut surface in the low speed ratio region to the medium speed ratio region, thereby reducing the torque capacity.
Here, the shape of the suction surface of the stator blade on which the cut surface is formed is substantially the same as the shape of the suction surface of the stator blade on which the cut surface is not formed, and the stator blade on which the cut surface is formed; There is no significant difference in fluid loss in the high speed ratio region of the stator blades that are not formed.

Therefore, by increasing the proportion of the stator blades having cut surfaces, the stator blades having the cut surfaces are arranged at an equal number of numbers relative to the basic blade type stator blades. By combining with a blade having a cut surface on the leading edge side, a peeled state can be positively generated at an extremely low speed ratio from the time of stall by the blade having the cut surface.
As a result, in the conventional torque converter, the inflection point of the torque capacity curve is two places including the inflection point due to the coupling. However, in the torque converter according to the present invention, the gear ratio is from the high speed ratio region. The torque capacity increases as it decreases toward the low speed ratio region, reaches a maximum value in the low speed ratio region, and then decreases toward the speed ratio = 0. Therefore, the torque capacity of the torque converter according to the engine output of the vehicle can be set.

Hereinafter, the torque converter according to the present embodiment will be described.
FIG. 1 is a longitudinal sectional view of a torque converter according to an embodiment.
A converter shell 11 is rotatably supported on a support shaft 10 on the transmission case side, and a pump impeller 12 is fixed to the converter shell 11. The converter shell 11 receives the output of an engine (not shown) on its input shaft 13. In the converter shell 11, the inlet side of the turbine runner 14 is disposed opposite the outlet side of the pump impeller 12 on the rotating outer peripheral side, and is coupled to a transmission input shaft 15 as an output shaft.

The stator 1 is interposed in the oil flow passage from the turbine runner 14 to the pump impeller 12 between the outlet side of the turbine runner 14 and the outlet side of the pump impeller 12 on the inner periphery of the rotation.
The stator 1 is supported on the support shaft 10 via a one-way clutch 16. The blades of the pump impeller 12 and the turbine runner 14 have a three-dimensional basic shape as before. Thus, a circulation path is formed in which the working oil flows in the direction indicated by the arrow when the pump impeller 12 rotates.

  Cores 17 and 18 are fixed to the pump impeller and the turbine runner, respectively, to improve the mounting rigidity of each blade row and to define the oil circulation path 19. In the figure, reference numeral 20 denotes a lock-up clutch mechanism. In order to house the lockup clutch mechanism 20 without increasing the axial length, the pump impeller 12 and the turbine runner 14 have a flat shape.

2 is an enlarged view in the direction of the AA direction in FIG. 1, FIG. 3 is an explanatory view for explaining the second stator blade, and FIG. 4 is a separation occurring in the first stator blade and the second stator blade. It is explanatory drawing explaining these.
The stator 1 is configured to include a first stator blade 1A and a second stator blade 1B at a predetermined ratio. In the stator 1, the first stator blade 1 </ b> A and the second stator blade 1 </ b> B are arranged around the rotation axis R.

The first stator blade 1A having the basic airfoil has a semicircular shape with a large curvature on the leading edge 1a side, a semicircular shape with a small curvature on the trailing edge 1b side, and the leading edge 1a and the trailing edge 1b are It has a blade cross-sectional shape connected by a pressure side 1c on the ventral surface side that draws a smooth and gentle curve, and a negative pressure surface 1d on the back side. Here, the intersection of the arc and the chord of the wing tip having an arbitrary radius of curvature becomes the leading edge point, and the wing provided with the chord having the arbitrary curvature of the leading edge point and the tip portion is defined as a basic wing shape. To do.
The first stator blade 1A is arranged in the stator 1 so that the front edge 1a is directed in the same direction as the axial direction of the rotation shaft R (input shaft 13) and the rear edge 1b is inclined in the rotation direction of the pump impeller 12. Is done.

The second stator blade 1B is a stator blade having a cut surface formed by cutting out a region from the negative pressure surface 1d including the front edge 1a of the first stator blade 1A to the positive pressure surface 1c.
As shown in FIG. 3, the second stator blade 1B has a point 1e moved from the front edge 1a of the first stator blade 1A to the rear edge 1b along the negative pressure surface 1d by a predetermined distance, and from this point 1e to the rotation axis. The first stator blade 1A is cut out along the line connecting the line V extending in the orthogonal direction and the intersection 1f of the pressure surface 1c.
Here, the point 1e is determined as a position where the separation distance L between the trailing edge 1b and the position 1e is the largest in the direction orthogonal to the rotation axis R of the stator.

A cut surface 1g formed by cutting out the first stator blade 1A along the line segment V is perpendicular to the rotation axis R of the stator when viewed from the radial direction of the stator.
The end surface 1e on the negative pressure surface 1d side and the end portion 1f on the positive pressure surface 1c side of the cut surface 1g are curved. For this reason, the position of the front edge of the second stator blade 1B is a position slightly shifted toward the rear edge 1b in the line segment connecting the position 1e and the rear edge 1b. The leading edge of the wing 1B is also expressed using the reference numeral 1e.

The second stator blade 1B is arranged in the stator 1 such that the cut surface 1g is directed in the same direction as the axial direction of the rotation axis R and the rear edge 1b is inclined in the rotation direction of the pump impeller 12.
At this time, when viewed from the radial direction of the stator, the inclination of the chord 1h of the second stator blade 1B from the rotation axis R direction is larger than the inclination of the chord 1i of the second stator blade 1B from the rotation axis R direction. State.
Here, the chord 1h means a line segment connecting the leading edge 1e and the trailing edge 1b of the second stator blade 1B, and the chord 1i connects the leading edge 1a and the trailing edge 1b of the first stator blade 1A. It means a connecting line segment.

The operation of the stator including the first stator blade 1A and the second stator blade 1B will be described.
FIG. 4 is a diagram for explaining the relationship between the flow of the working oil of the torque converter flowing into the stator and the relationship between the first stator blades 1A and the second stator blades 1B. (B) and (e) show the flow of hydraulic oil in the medium speed ratio range, and (c) and (f) show the flow of hydraulic oil in the high speed ratio range. Yes.

As shown in FIGS. 4A and 4D, in the low speed ratio region, the flow direction of the working oil is in a direction substantially perpendicular to the chords 1i and 1h of the first stator blade 1A and the second stator blade 1B. Therefore, the working oil flows around the front edge 1a of the first stator blade 1A and the front edge 1e of the second stator blade 1B, and then reaches the rear edge 1b side through the negative pressure surface 1d. .
At this time, a large separation occurs on each negative pressure surface 1d of the first stator blade 1A and the second stator blade 1B, but the vicinity of the front edge 1e of the second stator blade 1B is the vicinity of the front edge 1a of the first stator blade 1A. Is formed at an acute angle than the negative pressure surface 1d of the first stator blade 1A.

As shown in FIG. 4E, in the middle speed ratio region, in the case of the first stator blade 1A, the crossing angle between the flow direction of the working oil and the chord 1i of the first stator blade 1A becomes small. Therefore, since the working oil can reach the rear edge 1b side without largely flowing around the front edge 1a, the separation occurring on the suction surface 1d is smaller than in the case of FIG. 4 (d).
On the other hand, as shown in FIG. 4B, in the case of the second stator blade 1B, the crossing angle between the flow direction of the working oil and the chord 1h of the second stator blade 1B is larger than that of the first stator blade 1A. Is also big. For this reason, the amount of the working oil flowing around the leading edge 1e is larger than that in the case of FIG. 4E, so that larger separation than that in the case of the first stator blade 1A occurs on the suction surface 1d.

Furthermore, the cut surface 1g of the second stator blade 1B is positioned facing the flow direction of the working oil, and the flow direction of the working oil is greatly changed by the cut surface 1g so as to go around the front edge 1e. Since it reaches the trailing edge 1b side after flowing, peeling occurs on the suction surface 1d. Therefore, in the medium speed ratio region, the negative pressure surface 1d of the second stator blade 1B is separated due to the crossing angle between the flow direction of the working oil and the chord 1h and the separation caused by the cut surface 1g. .
Therefore, the separation that occurs on the suction surface 1d of the second stator blade 1B in the medium speed ratio region is greater than the separation that occurs on the suction surface 1d of the first stator blade 1A.

  As shown in FIGS. 4C and 4F, the shape of the suction surface 1d connecting the leading edge 1e and the trailing edge 1b of the second stator blade 1B is the trailing edge of the suction surface 1d of the first stator blade 1A. Since the shape on the 1b side remains, there is no significant difference in fluid loss in the high speed ratio region between the second stator blade 1B and the first stator blade 1A. Therefore, in the high speed ratio region, the flow direction of the working oil is a direction along the negative pressure surface 1d of the first stator blade 1A and the second stator blade 1B, and therefore, almost no separation occurs on each negative pressure surface 1d.

  As described above, the first stator blade 1A and the second stator blade 1B have different degrees of separation particularly in the medium speed ratio region. Therefore, in the stator including the first stator blade 1A and the second stator blade 1B, The torque capacity is lower than that of the stator having only the first stator blade 1A by the amount of separation that occurs in the second stator blade 1B.

FIG. 5 is a diagram showing a performance characteristic curve showing how the torque capacity changes according to the difference in the ratio between the first stator blade 1A and the second stator blade 1B.
In this figure, the symbol a indicates that the ratio of the first stator blade 1A and the second stator blade 1B is 1: 0, the symbol b is 2: 1, the symbol c is 1: 2, and the symbol d is 0. 1 shows a change in torque capacity in the case of 1.
FIG. 6 is an explanatory view illustrating a stator having a normal blade-type first stator blade 1A and a second stator blade 1B having a cut surface in a predetermined ratio. FIG. 6 (a) shows the stator 1 in the axial direction. (B) is an explanatory view for explaining the arrangement of the stator blades (first stator blade 1A, second stator blade 1B) arranged along the circumferential direction of the stator 1. FIG.

In the stator 1, the second stator blades 1 </ b> B are arranged in a predetermined number ratio with respect to the first stator blade 1 </ b> A of the basic blade type based on the torque capacity of the torque converter.
For example, when the ratio between the first stator blade 1A and the second stator blade 1B is 2: 1, as shown in FIG. 6A, the second stator blade 1B is interposed between the two first stator blades 1A. The stator blades are evenly arranged around the rotation axis so that only certain stator blades are not collected. Therefore, in the stator 1, the first stator blade 1 </ b> A and the second stator blade 1 </ b> B are arranged in the arrangement as shown in FIG. 6 (b) around the rotation axis with the leading edge side facing the turbine runner side (not shown). Placed in.
When the ratio between the first stator blade 1A and the second stator blade 1B is 1: 2, each stator blade is rotated by positioning the second stator blade 1B between the two second stator blades 1B. It is arranged evenly around the axis so that only certain stator blades do not collect.
That is, the second stator blades 1B are arranged at equal intervals with respect to the basic blade-type first stator blades 1A.

As shown in FIG. 5, as the ratio of the second stator blade 1B increases, the torque capacity at the time of stall (torque ratio = 0) and the torque capacity in the range from the low speed range to the medium speed range decrease. Further, since the stator includes the first stator blade 1A and the second stator blade 1B at a predetermined ratio, the degree of change in torque capacity in the range from the low speed ratio range to the medium speed ratio range becomes gentle. It can also be seen that the number of inflection points in the performance characteristic curve increases.
For example, in the torque capacity curve a when the ratio of the first stator blade 1A and the second stator blade 1B is 1: 0 and the torque capacity curve d when the ratio is 0: 1, the number of inflection points is respectively In the torque capacity curve b when the ratio is 1: 2 and the torque capacity curve c when the ratio is 2: 1, the inflection point is shown. The numbers increase to three locations indicated by reference numerals 1b, 2b, 3b and reference numerals 1c, 2c, 3c, respectively.

  As is apparent from the lower line segment in the figure, the difference in the ratio between the first stator blade 1A and the second stator blade 1B causes a slight difference in the low speed ratio region, but has a very large effect on the torque ratio. It turns out not to give.

As described above, in this embodiment, the torque including the pump impeller 12 and the turbine runner 14 that rotate about the common rotation axis R, and the stator 1 interposed in the oil flow passage from the turbine runner 14 to the pump impeller 12. In the converter, the stator 1 has a second cut surface 1g that is perpendicular to the rotation axis R formed by cutting out a region from the negative pressure surface 1d including the leading edge of the basic blade shape of the stator blade to the pressure surface 1c. The stator blades 1B are arranged at regular intervals with respect to the basic blade type stator blades 1A.
Here, in the second stator blade 1B formed with the cut surface 1g, the cut surface 1g faces the flow direction of the working oil when the speed ratio is in the range from the low speed ratio range to the medium speed ratio range. The first stator blade 1A that does not have a cut surface will cause greater separation from the low speed ratio range to the medium speed ratio range.
In addition, the shape of the suction surface 1d of the second stator blade 1B on which the cut surface 1g is formed is substantially the same as the shape on the trailing edge 1b side of the suction surface 1d of the first stator blade 1A on which the cut surface is not formed. Therefore, there is no significant difference in fluid loss in the high speed ratio region between the second stator blade 1B where the cut surface is formed and the first stator blade 1A where the cut surface is not formed.
Therefore, the second stator blade 1B having the cut surface 1g has a larger separation than the first stator blade 1A having no cut surface in the low speed ratio region to the medium speed ratio region, thereby reducing the torque capacity. .

Here, when the number of the second stator blades 1B in the stator 1 is increased, the torque capacity is reduced accordingly.
Therefore, by changing the ratio of the number of the second stator blades 1B and the first stator blades 1A in the stator 1, a torque capacity determined according to the ratio can be obtained, so that the ratio of the torque converter can be changed without changing the size of the torque converter. The target torque capacity can be obtained simply by changing the value.

In particular, the stator 1 has a configuration in which the second stator blade 1B having a cut surface is arranged at a predetermined ratio with respect to the basic blade type stator blade 1A based on the torque capacity of the torque converter. It can be set as the torque converter which can give a torque capacity characteristic.
In addition, the combination of the basic airfoil and the blade with the cut surface on the leading edge side can generate an exfoliation state at an extremely low speed ratio from the stall by the blade with the cut surface. In the torque converter, there are two inflection points in the torque capacity curve, including the inflection point due to the coupling. In the torque converter according to the present invention, the gear ratio is changed from the high speed ratio region to the low speed ratio region. As the torque decreases, the torque capacity increases, reaches a maximum value in the low speed ratio region, and then decreases toward the speed ratio = 0, resulting in a torque capacity characteristic having a plurality of inflection points.

Furthermore, the second stator blade 1B can reduce the torque capacity not only in the low speed ratio region but also in the medium speed ratio region, and the degree of change in the torque capacity in the region can be made gentle. Therefore, even if the torque capacity at the time of stall is reduced, the torque capacity does not increase abruptly when the speed ratio shifts from the low speed ratio area to the medium speed ratio area.
Therefore, even if the torque capacity at the time of stalling is reduced, the driver does not feel an uncomfortable feeling of acceleration. Therefore, the torque capacity at the time of stalling can be lowered to improve the fuel efficiency of the idle engine.

A first modification of the second stator blade will be described.
FIG. 7 is an explanatory diagram illustrating the second stator blade according to the first modification, and FIG. 8 is an explanatory diagram illustrating the torque capacity characteristics of the second stator blade according to the first modification.
In FIG. 8, the line segments denoted by reference numerals b, c, and d are formed by cutting the first stator blade 1A along the line segments b, c, and d in FIG. The torque capacity characteristics of the second stator blade are shown respectively.

In the above embodiment, when the cut surface perpendicular to the rotation axis is formed, the position of the end 1e is determined so that the width L of the second stator blade is the widest (see FIG. 3).
In the second stator blade 1C according to the first modification, the diameter Y of the inscribed circle in contact with the suction surface 1d of the second stator blade and the pressure surface 1c near the trailing edge 1b of the adjacent stator blade is not changed. The cut surface is formed by moving the position of the end portion 1f on the pressure suppression surface 1c side to the rear edge 1b side.

As shown in FIG. 7, stator blades having different widths in the direction of the rotation axis are obtained by cutting out the region including the leading edge of the first stator blade along a line segment orthogonal to the rotation axis indicated by reference numerals b, c, d It can be seen from the torque capacity characteristic curve of FIG. 8 that the torque capacity decreases as the stator blade (the stator blade having a shorter width in the rotation axis direction R) whose end portion 1f is located on the trailing edge 1b side.
Therefore, the target torque capacity can be obtained only by changing the range of notching the stator blades without changing the size of the torque converter.

A second modification of the second stator blade will be described.
FIG. 9 is an explanatory diagram illustrating a second stator blade according to a second modification, and FIG. 10 is an explanatory diagram illustrating a torque capacity characteristic of the second stator blade according to the second modification.
In FIG. 10, the line segments denoted by symbols b, c, and d are formed by cutting the first stator blade 1A along the line segments b, c, and d in FIG. 9. The torque capacity characteristics of the second stator blade are shown respectively.

In the above embodiment, the second stator blade is formed by cutting out the front edge side of the first stator blade so that a cut surface perpendicular to the rotation axis is formed.
In the second stator blade 1D according to the second modification, the diameter Y of the inscribed circle in contact with the pressure surface 1c of the second stator blade and the suction surface 1d near the trailing edge 1b of the adjacent stator blade is not changed. The position of the end portion 1f on the positive pressure surface 1c side of the cut surface is moved to the rear edge 1b side.

As shown in FIG. 9, when the first stator blade is cut out along the lines b, c, and d to form a stator blade having a cut surface, the position of the end 1f is on the trailing edge 1b side. It can be seen from the torque capacity characteristic curve of FIG. 10 that a certain stator blade (a stator blade having a smaller crossing angle between the cut surface and the rotating shaft) has a lower torque capacity.
Therefore, the target torque capacity can be obtained only by changing the position where the stator blades are cut out without changing the size of the torque converter.

In the above-described embodiment, the stator is provided with the second stator blade 1B having a cut surface perpendicular to the rotation axis and the first stator blade 1A having no cut surface at a predetermined ratio. Although described as an example, the second stator blade combined with the first stator blade 1A may be used as the second stator blade 1C according to the first modification described above or the second stator blade 1D according to the second modification. good. Moreover, it is good also as a stator comprised including these 2nd stator blade | wing 1B, 1C, 1D by arbitrary ratios.
Thereby, it can be set as the torque converter which can give the torque capacity characteristic with many inflection points compared with the conventional torque converter.
Therefore, a torque converter that can provide torque capacity characteristics tailored to the vehicle can be provided by changing the combination of the stator blades.

FIG. 11 is a diagram illustrating a stator blade according to a third modification.
In the above embodiment, the case of the stator blade in the case where the cut surface 1g is a plane as shown in FIG. 11A has been described as an example.
However, the cut surface is not limited to a flat surface, and may have a streamlined shape in a sectional view. For example, as shown in FIG. 11B, a cut surface in a range from the front edge 1e to the end 1f ′ on the front edge 1e side of the pressing surface 1c may be a smooth surface curved in a streamline shape in a cross-sectional view. good.
Also in the case of this stator blade 1E, the smooth surface 1g ′ faces the flow direction of the working oil in the range from the low speed ratio range to the medium speed ratio range. Torque capacity can be reduced.

It is a figure explaining the torque converter concerning an Example. It is a figure explaining the stator blade | wing concerning an Example. It is a figure explaining the stator blade | wing concerning an Example. It is explanatory drawing explaining the flow of the fluid with respect to a stator blade | wing. It is a figure which shows the performance characteristic curve of a torque converter provided with the stator blade | wing concerning an Example. It is explanatory drawing explaining the stator provided with the stator blade | wing concerning an Example by arbitrary ratios. It is a figure explaining the stator blade | wing which concerns on a 1st modification. It is a figure which shows the performance characteristic curve of a torque converter provided with the stator blade | wing which concerns on a 1st modification. It is a figure explaining the stator blade | wing which concerns on a 2nd modification. It is a figure which shows the performance characteristic curve of a torque converter provided with the stator blade | wing which concerns on a 2nd modification. It is a figure explaining the stator blade | wing concerning a 3rd modification. It is a figure which shows the stator blade | wing of the torque converter which concerns on a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Stator 1A 1st stator blade 1B, 1C, 1D 2nd stator blade 1a, 1e Lead edge 1b Trail edge 1c Pressure surface 1d Negative pressure surface 1g Cut surface 1h, 1i Blade chord 10 Support shaft 11 Converter shell 12 Pump impeller 13 Input shaft 14 turbine runner 15 transmission input shaft 16 one-way clutch 20 lock-up clutch mechanism

Claims (2)

In a torque converter comprising a pump impeller and a turbine runner that rotate about a common rotation axis, and a stator interposed in an oil flow passage from the turbine runner to the pump impeller,
In the stator, a cut surface perpendicular to the rotation axis formed by cutting out a region including the front edge in the basic airfoil of the stator blade, or a front edge side end of the pressure surface is a front edge side end of the suction surface A torque converter characterized in that stator blades having cut surfaces inclined so as to be on the downstream side in the oil flow direction are arranged at equal numbers with respect to the basic blade-type stator blades. 2. The torque according to claim 1, wherein the stator blades having the cut surfaces are arranged in a predetermined number ratio with respect to the stator blades of the basic blade type based on the torque capacity of the torque converter. converter.

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