JPS61212682A - Variable capacity pump device - Google Patents

Abstract

PURPOSE:To enable the reduction of pump power by connecting the stator shaft extending from the stator of a torque converter to the cam ring of a variable capacity vane pump so that the discharge rate of the pump can be changed in response to the reaction of the stator. CONSTITUTION:The cam ring 12 of a variable capacity vane pump is energized by a spring 19 fitted to a housing 3 in such direction as the capacity is decreased, and further connected to a stator shaft 21 extending from the stator of a torque converter via a slide pin 17. Consequently, since the cam ring moves in response to the reaction of the stator of torque converter to change the discharge rate of the pump, wasteful drive of pump can be avoided and pump power can be reduced to a great extent.

Description

DETAILED DESCRIPTION OF THE INVENTION (A) Field of Industrial Application The present invention relates to a variable displacement pump consisting of a vane type pump, and more particularly to an oil pump device provided in a vehicle automatic transmission using a torque converter.

(B) Prior Art Generally speaking, constant displacement gear pumps are used as oil pumps of this type because they have a small number of parts and are low cost.

However, the discharge amount of the gear pump is proportional to the pump rotation speed, that is, the engine rotation speed, but the pump capacity is set to ensure a sufficient discharge amount even at low speeds, especially when idling, and when driving at high speeds. During high-speed rotation, a large amount of excess discharge was generated, which was being released through the relief valve. Therefore, extra pump power was consumed, which had a negative effect on the fuel efficiency of the vehicle.

Therefore, recently, attempts have been made to use vane type variable displacement oil pumps in some vehicle transmissions. The variable displacement pump is configured such that the pump displacement is made variable by swinging a slide, and the back surface of the slide is connected to the drain pressure of a pressure regulator valve. Thereby, the pressure discharged from the pump is regulated by the pressure regulator valve to a predetermined line pressure according to the throttle opening, and the pump discharge amount is regulated by the drain pressure drained from the valve.

(c) Problems to be Solved by the Invention Therefore, since the variable displacement pump is regulated by the drain pressure of the pressure regulator valve, unless the line pressure is optimally controlled to the required minimum pressure, Pump output is not optimally controlled.

By the way, ideally the line pressure would be controlled according to the input torque to the transmission, but in the past it was controlled by the throttle opening instead, so the line pressure was not necessarily set to the optimal value. Therefore, the discharge amount control of the variable displacement pump cannot be said to be optimal.

Furthermore, since the pump discharge amount is controlled by hydraulic control, there is a possibility that valve sticking and oil leakage may occur.

Furthermore, since the pump discharge amount is controlled by the pressure regulator valve, the pump discharge amount control circuit is complicated with other control circuits, and is not disturbed by other control circuits such as the valve stick of the throttle valve. There is a possibility that

Therefore, the present invention solves the problem of the variable displacement oil pump mentioned above.
The object of the present invention is to solve the above problems and provide a variable displacement pump device that is compact, low cost, and highly reliable.

(b) Means for solving the problem The present invention has been made in view of the above circumstances, and is
As shown in the figure and FIG.
The arm 20 is further connected and fixed to a stator shaft 21 extending from the stator of the torque converter.

(E) Effect Based on the above configuration, when the reaction force acting on the stator is large (for example, at the start of running), the slide 12 is swung against the spring 19 via the stator shaft 21 and the stator arm 20, and the eccentricity is reduced. Increase the pump output by increasing the volume. Then, the swinging position of the slide 12 is set to a position where the stator reaction force and the slide return spring 20 are balanced, and the pump discharge amount is adjusted according to the stator reaction force.

(F) Embodiments Hereinafter, embodiments of the present invention will be described with reference to the drawings.

The variable displacement pump device 1 has a pump body 3 provided within a torque converter housing 2, as shown in FIGS. 1 and 2. Further, an impeller hub 6 of a torque converter extends inside the center of the body 3 in an oil-tight manner with an oil seal 5, and a rotor 7 is fixed to the hub 6. Moreover, the rotor 7 has a large number (
7) vanes 9 are fitted so as to be slidable in the radial direction, and these vanes 9 are floatingly supported by abutting left and right cam rings 10, 10 at their center side ends. On the other hand, a pivot pin 1 is attached to the outer periphery of the pump body 3.
1 is implanted, and a slide 12 is swingably supported by the pin 11.

The slide 12 has an annular shape, and the vane 9 is in sliding contact with the inner circumferential wall of the annular ring, and a discharge port 13 and an inlet port 15 are formed across the housing 2 at the upper and lower parts of the inner circumferential wall. Furthermore, the outer circumferential portion of the slide 12 away from the robot pin 11 has an outer surface.

A lug 16 is formed to protrude toward the housing 2, and a slide pin 17 is implanted in the lug 16, and a slide return spring 19 is compressed between the lug 16 and the shoulder portion of the housing 2. The slide pin 17 passes through a long hole 2a formed in the housing 2 and protrudes to the outside, and the stator arm 20 is brought into contact with and connected to the side surface opposite to the biasing force of the spring 19 at the protrusion. The stator arm 20 is connected and fixed to a stator shaft 21 extending to the center of the pump device 1. Further, the stator shaft 21 is rotatably supported within the housing 2 and the impeller 8 by bushings 22, etc.
It is connected to the stator of the torque converter via a one-way clutch.

In the figure, 23 is a stopper pin that restricts the return position of the slide 12, and 25 is a sealing member such as an O-ring.

Since the present embodiment has the above-described configuration, when the rotor 7 is rotated via the impeller 8 based on the rotation of the pump impeller of the torque converter, a large number of vanes 9 are also integrated with the rotor 7. be rotated.

At this time, the vane 9 is floatingly supported by the two left and right cam rings 10, and is in sliding contact with the slide inner wall regardless of the swinging position of the slide 12.
Based on the amount of damage d of the rotor 7 relative to the rotation of the vane 9, oil is sucked in from the suction port 5 and is discharged from the discharge port 13. The discharged oil is regulated to line pressure by a pressure regulator valve, controls each clutch and brake of the planetary gear set, and is supplied within the automatic transmission as lubricating oil for the gear set.

The discharge amount of the variable displacement pump device 1 is determined by the rotor 7.
The position of the slide 12 is adjusted by the amount of eccentricity of the slide 12, that is, the swinging position of the slide 12.
It is controlled by a stator shaft 21 via a pin 17 and a stator arm 20. That is, in the converter range of the torque converter, a reaction force proportional to the input torque of the automatic transmission acts on the stator, and the point where the stator reaction force and the resistance force of the return spring 19 are balanced is the slide 12.
It will be in the swing position. Therefore, as shown in FIG. 3, at the start of running, that is, in a region where the pump rotation speed is low based on the rotation of the impeller hub 6, a large reaction force acts on the stator, and the slide 12 is largely eccentric against the spring 19. In this position, the pump device 1 discharges the maximum amount (maximum discharge amount region A).

Then, when the pump rotation speed increases in proportion to the running speed, the reaction force acting on the stator decreases, the slide 12 moves so that its eccentricity becomes smaller, and the discharge amount gradually decreases (discharge amount change Area B).

Furthermore, when the traveling speed increases and exceeds the clutch point (coupling range), the reaction force no longer acts on the stator, the slide 12 comes to the minimum eccentric position in contact with the stopper pin 23, and the pump device 1 also reaches the minimum discharge. amount (minimum discharge amount area C). Therefore, while the conventional constant displacement pump has an increased discharge amount compared to the pump rotation speed as shown by (■), the pump device of this embodiment has a
As shown in (2), even if the pump rotation speed increases, the discharge amount does not increase, and the amount of discharge indicated by diagonal lines, which was wasted in the past, can be saved.

Next, a partially modified embodiment will be described based on FIG. 4.

This embodiment attempts to simultaneously obtain a discharge amount and line pressure proportional to the stator reaction force by adjusting the pump discharge amount and the pressure regulator valve.

That is, the pressure regulator valve 30 is disposed facing the pump device 1, and is configured such that the end portion 30a of the valve 30 abuts the tip fi portion 20a of the stator arm 20. In the figure, 31 is a reefer relief valve, and 32 is a strainer.

Therefore, the pressure regulator valve 30 is strongly pushed by the stator arm 20, and the suppressing force is equal to the stator reaction force minus the reaction force of the return spring 19. As a result, pressure regulator valve 3
o is directly controlled by the stator reaction force, which is proportional to the input torque of the automatic transmission. Adjust to

Next, another embodiment will be described based on FIG.

For example, in a belt-type continuously variable transmission (CVT), a large amount of hydraulic oil is required during a kickdown shift, and in such a case, the large amount of hydraulic oil is The discharge amount is increased in advance according to a computer command before it is required.

The rod 35 is connected to the slide pin 17 and the pump device 1
The piston 37 of the hydraulic cylinder device 36
Connect to. Further, the oil discharged from the discharge port 13 is supplied to the line pressure via the pressure regulator valve 30, and communicates with the pressure modulator valve 39 via the orifice 37, and further from the valve 39 to the oil chamber 36a of the hydraulic cylinder device 36. is connected to. Further, a solenoid valve 40 is disposed branching off at a position m above the pressure modulator valve 39, and the solenoid valve 40 is opened and closed by instructions from a computer.

Since this embodiment has the above-described configuration, the solenoid valve 40 is open in the normal state, and the oil chamber 36 is opened.
Pressure oil is not supplied to a.

Therefore, in this state, the slide 12 is swung by the stator reaction force and the pump discharge amount is adjusted, as in the previously described embodiment. And when a large amount of hydraulic oil is required,
When necessary, the solenoid is turned on and the solenoid valve 40 is closed according to a command from the computer. Then, the line pressure is reduced by the pressure modulator valve 39, the reduced pressure is supplied to the oil chamber 36a, the piston 37 of the cylinder device 36 moves in the direction of the arrow, and the slide 12 swings greatly via the rod 35. move. Thereby, the pump device 1 is adjusted to the maximum discharge amount, and can cope with an increase in the operating amount of CvT or the like, regardless of the stator reaction force.

(g) As described in detail, according to the present invention, since the slide 12 is oscillated based on the stator reaction force, it is possible to obtain a pump discharge amount that is accurately proportional to the transmission input torque. Therefore, the pump device 1 can always discharge only the minimum necessary amount of oil, reduce pump drive loss, and improve fuel efficiency of vehicles. In addition, since the slide 12 is linked to the stator shaft 21, the pump discharge amount can be controlled by simple mechanical control, improving reliability and reducing costs. Since it is completely separate and independent from the control section, it is not affected by malfunctions that occur in other control sections, and stable pump discharge amount control can be performed.

[Brief explanation of drawings]

Fig. 1 is a diagram taken along line II in Fig. 2 showing a variable displacement pump device according to the present invention, Fig. 2 is a sectional view taken along line ■-■ in Fig. 1, and Fig. 3 is a diagram showing the functions of the present invention. , FIG. 4 is an overall schematic diagram showing a partially modified embodiment, and FIG. 5 is an overall schematic diagram showing another embodiment. DESCRIPTION OF SYMBOLS 1... Variable displacement pump, torque converter housing, 3... Pump body, 7... Rotor, 9... Vane, 11... Pivot pin, 12... Slide, 13... Discharge port , 15... Suction port, 17... Slide pin, 19... Slide return spring,
20... Stator arm, 31... Stator shaft. Applicant: Aisin Warner Co., Ltd. Figure 3/Ni6a Nimaki (Rpm) Figure 2

Claims (1)

[Claims] (1) A variable displacement pump device that is installed facing a torque converter and includes a rotor that slidably supports a large number of vanes in the radial direction, and a slide that is swingably supported by a pump body. A variable displacement pump device characterized in that a stator shaft extending from a stator is interlocked with the slide to control swinging of the slide based on a stator reaction force.