JPS60220259A - Hydraulic torque converter - Google Patents

Abstract

PURPOSE:To constitute the titled converter so that only when the number of rotation of the turbine is zero and an accelerator pedal is not stepped down, a capacity coefficient which is lower than that at other times is exhibited, by forming a stator by a movable vane having a stationary vane and spring means. CONSTITUTION:A stator 14 has a stationary vane 8, and a movable vane 13 which is movable between a first position provided at the inlet part of the stator 14 and extended in a direction along the flow of a working fluid which flows into the stator 14 when the speed ratio is less than a predetermined value and a second position extended in a direction intercrossing the flow of the working fluid. The movable vane 13 is actuated from the first position to the second position by a resilient force exerted by spring means. When the speed ratio is less than a predetermined value, the movable vane 13 is moved from the second position to the first position against the resilient force of the spring means in accordance with the increase in the flow speed. Thus, only when the number of rotation of the turbine is zero and the accelerator is not stepped down, a capacity coefficient which is lower than that at other times is exhibited.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a hydraulic torque converter, and more particularly to a hydraulic torque converter used in automatic transmissions for vehicles.

The hydraulic torque inverter used in the invention is generally of the three-wheeled two-phase type including a pump/turbine and a stator, and is used for i-lux variable operation. and a fluid coupling action.

The fluid-type converter used in automatic transmissions for vehicles has a capacity coefficient C - pump torque 11 / (pump rotation speed N1
)2 is large, and on the other hand, when the vehicle is stopped during traffic lights, etc.+)-1, the stall torque ratio is required to be small and the capacity coefficient O is required to be small during this idling operation. However, in a conventional general hydraulic torque converter, all the blades installed on each blade are fixed, so the capacity coefficient C is the speed ratio e - turbine rotation speed N27/
It is uniquely determined by (pump rotation speed N+)', and at the same speed ratio, it is the same regardless of the change in pump rotation speed N1. If the capacity coefficient C when a=Q is set to a relatively large value, the capacity coefficient G during idling operation must be the same relatively large value as the capacity coefficient C when the vehicle starts. do not have.

If the capacity coefficient C of the hydraulic torque converter is large during idling, the driving torque of the internal combustion engine is large to drive the pump of the hydraulic torque converter, and the engine rotational speed during range stalling accordingly increases. As a result, vibration due to fluctuations in the rotation of the internal combustion engine becomes large, and there is a risk that the vibration and noise performance of the vehicle will deteriorate. In order to avoid deterioration of vibration and noise performance, it is possible to increase the engine speed during idling operation, but as the engine speed increases during idling operation, the creep force increases and the fuel economy of the internal combustion engine decreases. Sexuality worsens.

In view of the above-mentioned problems with conventional hydraulic torque converters, we developed a variable capacity hydraulic torque converter in which the stator is provided with movable vanes and the capacity coefficient changes depending on the position of the movable vanes!・An inverter has already been proposed, and one of them, as already proposed in JP-A-58-113658, has a stator with fixed blades and movable blades, and has a pump and a turbine. When the flow rate of the working fluid flowing through the annular truss formed by the stator is below a predetermined value, the movable blades are out of alignment with the fixed blades, and when the flow rate of the working fluid is above a predetermined value, the movable blades are aligned with the fixed blades. During idling operation, where the pump rotational speed is low and the flow velocity of the working fluid does not exceed the predetermined value, the movable blade is out of alignment with the fixed part (2), thereby reducing the capacity coefficient. ing. In this hydraulic torque converter, the intended purpose of lowering the capacity coefficient during idling operation is achieved, but when the flow rate of the working fluid is below a predetermined value, regardless of the speed ratio at that time. Because the movable wing is out of alignment with the fixed wing,
As is generally well known, even when the flow velocity of the working fluid decreases as the speed ratio approaches 1, the movable blades may become out of alignment with the fixed blades and the torque capacity decreases. When the phase ratio is close to 1, the slippage in the hydraulic torque converter increases during normal driving, resulting in a problem that the fuel economy of the internal combustion engine deteriorates.

Purpose of the Invention The present invention provides a capacity coefficient that is lower than at other times only when the vehicle is idling at a stop such as at a traffic light, in other words, when the turbine rotation speed is O and the accelerator pedal is not depressed. It is an object of the present invention to provide an improved hydraulic torque converter that exhibits the following characteristics.

According to the present invention, the above-mentioned object is to provide a hydraulic torque converter including a pump, a turbine, and a stator, in which the stator has fixed blades and a stator inlet. movable between a first position extending in a direction along the flow of working fluid flowing into the stator when the ratio is less than a predetermined value and a second position extending in a direction transverse to the flow of the working fluid; 5- movable blades, the movable blades being urged from the first position toward the second position by the spring force of the spring means, and when the speed ratio is below a predetermined value, the working fluid is This is achieved by a hydraulic torque converter which is configured to move from said second position d towards said first position against the spring force of said spring means in response to an increase in flow velocity.

Effects of the Invention According to the configuration as described above, the movable blades extend in a direction transverse to the flow of the working fluid flowing into the stator when the speed ratio is below a predetermined value, and are pressurized by the working fluid,
When the flow rate of the working fluid is low, that is, during idling operation with a low pump rotation speed, the pressure is overcome and the working fluid is held in the second position by the spring force by the spring means, and at this time the working fluid flows from the turbine to the stator. Restrict fluid flow. In addition, during re-idling operation, the capacity coefficient and torque ratio are reduced, the stall and torque ratios are reduced, the creep force is reduced, and the engine speed decreases less during range stalling.6- By reducing the torque fluctuation of the internal combustion engine, the engine speed during idling operation can be set low, and the fuel economy of the internal combustion engine can be improved.

When the II vehicle starts, the pump rotational speed increases as the engine rotational speed increases due to the depression of the accelerator pedal, and the flow velocity of the working fluid increases. The spring force moves it from the second position to the first position and substantially impedes the flow of working fluid into the stator, thus increasing the capacity coefficient and providing smooth starting.

Since the inflow direction of the working fluid flowing into the stator changes depending on the speed ratio, when the speed ratio is greater than or equal to the predetermined value, the working fluid flows toward the movable blades in a direction from the second position to the first position. Therefore, the movable vanes are always in the second position when the speed ratio is above the predetermined value, and at this time, the movable vanes substantially control the flow of the working fluid flowing into the stator. Therefore, when the speed ratio is above a predetermined value, that is, during normal driving, the capacity coefficient and torque capacity do not decrease.

DESCRIPTION OF EMBODIMENTS The present invention will now be described in detail with reference to embodiments with reference to the accompanying drawings.

FIG. 1 shows one embodiment of a hydraulic torque converter according to the present invention. In the figure, 1 indicates a front cover, and 2 indicates a pump outer shell fixedly connected to the front cover 1.

A flywheel 4 is fixedly connected to the front cover 1 by screw fastening means 3, and a crankshaft 6 for internal combustion AVA is fixedly connected to the flywheel by screw fastening means 5.

Inside the torque converter chamber 7 defined by the front cover 1 and the pump outer shell 2, a pump 9 constituted by a plurality of fixed blades 8 fixed to the pump outer shell 2 and a plurality of fixed blades 10 are installed. and a stator 14 having a plurality of fixed blades 11 and a plurality of movable blades 13. The turbine 11 is connected to an output shaft 16 by a hub member 15 in a torque transmitting relationship. The stator 14 is supported by the output shaft, and the stator 14 connects its hub portion 14a to the fixed shaft 1 via the one-sided clutch 17.
8 and supported by the fixed shaft, and can rotate about the fixed shaft 18 only in the same direction as the pump 3. A working fluid such as oil is encircled within the torque converter chamber 7.

In the illustrated embodiment, a direct coupling clutch 21 including a shock absorber 19 and a clutch piston 20 is provided in the torque converter chamber 7 .

As clearly shown in FIG. 2, the stator 14 has a plurality of fixed blades 12 at equal intervals around its circumference, and furthermore, each stator blade 14 has a plurality of fixed blades 12 arranged at equal intervals around the circumference thereof, and each stator blade 12 has a plurality of fixed blades 12 arranged at an inlet portion of the working fluid between adjacent fixed blades 12. A movable wing 13 pivotally supported by a pivot 13a is rotatably provided. The movable blades 13 move the stator 1 when the speed ratio e is below a predetermined value, that is, below a small value close to 0 or O.
4, and a second position extending in a direction transverse to the working fluid flow S+, Compression springs 22 provided between each fixed blade 12
The spring force is biased toward the second position from the first position.

FIG. 3 shows the operating principle of a hydraulic torque converter and an interpolated three-element two-phase hydraulic torque converter according to the invention. In Fig. 3, S represents the absolute flow of the working fluid flowing through the annular truss composed of the pump, the turbine 11, and the stator 14, the dashed line represents the relative flow of the working fluid in each element, and the zero weight represents the pump. 9 is the circumferential speed, ω2 is the circumferential speed of the turbine 11, Fl is the force acting on the pump 9 from the working fluid, [2 is the force acting on the turbine 11 from the working fluid, F8 is the force acting on the stator 14 from the working fluid. The acting force is TI, and the torque (input torque) of the pump 9 is ・T2
T8 indicates the torque of the turbine 11 (output torque), and T8 indicates the torque of the stator 14, respectively.

The working fluid in the annular truss constituted by the pump 9, the turbine 11, and the stator 14 flows through the annular truss in an absolute flow S as the pump 9 is driven by the internal combustion engine to rotate in the same direction as the engine rotation direction.
The working fluid flows as shown in FIG.
is applied to the turbine 11, and by flowing out from the pump 9 and flowing into the turbine 11, the turbine torque in the opposite direction to the pump torque king 1, that is, in the same direction as the engine rotation direction, is generated.
is applied to the turbine 11, flows out from the turbine 11 and flows into the stator 14, imparts to the stator 14 a pump torque - a stator torque (reaction force) T3 in the same direction, and is applied by the fixed inner part 12 of the stator 14. The flow direction is deflected and flows back into the pump 9 in the same direction as the pump rotation direction.The flow direction of the hydraulic oil flowing into the stator 14 from the turbine 11 is determined by the speed ratio e, as shown in FIG. The smaller the speed ratio e is, that is, when it is closer to O, the flow will flow from the direction opposite to the front of the fixed wing 12, as shown by the flow line S1, and the speed ratio e will be 0.5. Sometimes it flows in a direction substantially along the extending direction of the stator blade 12 as shown by a flow line S2, and as the speed ratio e increases further, it flows to the back surface of the stator blade 12 as shown by a flow line S3. When the working fluid flows into the squirrel data 14 in the direction facing the back side of the fixed v!J12, the stator 1/1 is in the 11j direction clutch 17 (see Figure 1) is in a free state. As a result, the pump 9 and the turbine 11 can rotate in the same direction as the pump 9 and the turbine 11 with respect to the fixed shaft 18.

The movable vanes 13 of the stator 14 extend in a direction transverse to the flow SI of the working fluid flowing into the stay 914 when the speed ratio is 01fiO or a small value close to O. Therefore, when the speed ratio 0 is near 0, that is, when the vehicle is stopped, the pump rotation speed is low, that is, the engine rotation speed is low, and the flow speed of the working fluid flowing through the annular truss is low. When it is less than the predetermined value 11+, the low force acting on the movable blade 13 from the working fluid in the direction from the second IQ position toward the first position is relatively small, so that the movable blade 13 compresses the compression coil. 40 FI in the second position by the spring force of the spring 22
Maintain the R status. Therefore, during idling when the vehicle is stopped J2, the movable blade 13 is located at the second position, so that the flow of the working fluid flowing through the annular truss is suppressed, and the outflow of this working fluid is reduced. As a result, the capacity coefficient C decreases with the torque ratio λ, as shown by the broken line in FIG.

When the vehicle starts, the accelerator pedal is depressed and the engine speed increases, which increases the pump rotation speed.As a result, the flow velocity of the working fluid flowing through the annular truss increases, and as a result, the working fluid moves more. As the pressure applied to the blade 13 increases, the movable blade 13 moves the compression coil spring 22 from the second position to the first position as the pressure increases, in other words, as the engine speed increases. It is rotationally displaced against the force and is positioned at a position that does not impede the flow of the working fluid flowing through the annular truss. At this time, as the flow rate of the working fluid flowing through the annular truss is restored, both the capacity coefficient C and the torque ratio λ increase, and the capacity coefficient C and the torque ratio λ are both determined by the fixed blade 12.
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When the speed ratio O increases, the direction of inflow of the working fluid into the stator 14 changes as described above, and the movable! 11!12 indicates the flow S? of the working fluid flowing into the stator 14 even if it is located at the second position? ~S3 substantially extends in a non-uniform direction, and at this time, the working fluid flows through the annular truss because no pressure is applied in the direction from the second position to the first position. Regardless of the flow rate of the working fluid, it is always positioned at the second position, and the flow of the working fluid is not impaired.

Therefore, at this time, the 1 to 1 torque capacity of the hydraulic torque converter is not reduced.

The change in capacity coefficient due to the movable blade 13 having the above-mentioned configuration is quite large, and therefore, the movable blade 13 does not have to cover all the areas between the fixed parts 11912 adjacent to each other.

Although the present invention has been described above in detail with reference to specific embodiments, the present invention is not limited thereto, and various embodiments are possible within the scope of the present invention. This should be obvious to those in question.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view showing one embodiment of the hydraulic torque converter according to the present invention, FIG. 2 is a cross-sectional view showing a winding turbine of the hydraulic torque converter according to the present invention, FIG. Fig. 4 is a principle diagram showing the operating principle and flow of working fluid in a three-line two-phase hydraulic torque converter, and Fig. 5 shows the capacity coefficient characteristics and torque ratio characteristics with respect to the speed ratio of the hydraulic torque converter. This is a graph showing. 1...Fent cover, 2...Pump outer shell. 3... Screw fastening means, 4... Flywheel, 5...
... Screw fastening means, 6... Crankshaft of internal combustion engine, 7
...Torque converter chamber, 8...Fixed wing, 9...
Pump, 10... Fixed blade, 11... Turbine, 12
... Fixed wing, 13... Movable wing, 14... Stator, 15... Hub member. 16...Output shaft, 18...Fixed shaft, 19...Loose W
J device. 20...Clutch piston, 21...Direct clutch. 22... Compression coil spring patent applicant Toyota Auto China Co., Ltd. Representative Patent attorney Masatake Akashi 2 Figure 14 Figure 5 JP-A-2002-59 (6) Figure 3''■1・~11 12 12 12 U14 2 C1

Claims (1)

[Claims] In a hydraulic torque converter including a pump, a turbine, and a stator, the stator is installed at the inlet of the stator and is connected to the flow of working fluid flowing into the stator when the speed ratio is below a predetermined speed ratio. a re-rotating blade movable between a first position extending in a direction along the working fluid and a second position extending in a direction transverse to the working fluid; is urged toward the second position from the first position by the spring means, and when the speed ratio is less than a predetermined value, the spring force of the spring means is resisted in response to an increase in the flow velocity of the working fluid. 1. A hydraulic torque converter, wherein the hydraulic torque converter is configured to move from the second position to the negative position.