JPH10306783A - Balanced type vane pump structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To obtain oil delivery pressure required at the time of starting a pump positively in a short time by suppressing sliding resistance low. SOLUTION: In a balanced type vane pump 1, a rotor 4 with vanes 5 fitted into vane grooves 15 is built in a housing 2. This vane pump 1 is provided with a guide plate 17 coming in contact with a vane back part of each vane 5 so as to push the vane 5 radially outward from the rotation axis of the rotor 4 in association with the rotation of the rotor 4. This guide plate 17 can also be so formed that the vane back part of the vane 5 comes in contact in a position of facing an intake port 8.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of a balanced vane pump used for a hydraulic device such as an industrial machine or an automobile device.

[0002]

2. Description of the Related Art In general, an equilibrium vane pump has a housing having a substantially elliptical pump chamber therein, a rotor rotatably housed in the housing, and an equidistant and reciprocally movable vane groove of the rotor. And a vane provided at the bottom. In this configuration, when the rotor accommodated in the housing rotates, the vane is pushed out from the outer periphery of the rotor and rotates while sliding on the inner peripheral surface of the housing. As a result, the pump space (partitioned by the outer peripheral surface of the rotor, two adjacent vanes, and the inner peripheral surface of the pump chamber) partitioned by each vane in the pump chamber becomes larger, and the oil is sucked. Discharges oil while becoming smaller.

[0003] In this case, the vane always repeats the retracting operation with the rotation of the rotor, and the outer diameter end of the vane needs to move while sliding on the peripheral surface of the pump chamber. In order to make this retracting operation possible, the vane is biased in a direction protruding from the rotor. As a means for urging the vane, there is a method in which a hydraulic pressure generated by the balanced vane pump itself is applied to an inner peripheral end portion of the vane, and the hydraulic pressure is used as a protruding pressure of the vane. In some cases, a spring is provided at the back of the vane (inner end) to push the vane by the spring force.

[0004]

However, when the hydraulic pressure generated by the balanced vane pump itself is used as the vane protrusion pressure as in the conventional balanced vane pump having the above-described structure, the operation of the vane is started when the pump is started. There is a problem that it tends to be unstable. This is because when the rotor is stopped, the vane located above the rotor is drawn into the vane groove by its own weight, and the pump space for creating pressure is open at the vane tip (outer diameter side end). . For this reason, in the initial stage of the rotation of the rotor, since oil leaks through this open portion, it is not possible to produce sufficient pressure, and it is necessary to supply sufficient pressure to the back of the vane. become unable.
As a result, the discharge pressure becomes synergistically unstable, and it takes a long time to obtain the oil discharge pressure required for the balanced vane pump.

[0005] This problem tends to occur particularly when the equilibrium vane pump is started in a place where the temperature is low such as a cold region. That is, when the temperature is low, the viscosity of the oil is high, and the vane is difficult to move in the vane groove. For this reason, when the balanced vane pump is started, it takes time for the vane drawn into the vane groove to be discharged and to generate a pressure sufficient to allow the vane to move in and out smoothly. As a result, there is a problem that it takes time to obtain the oil discharge pressure required for the balanced vane pump. This problem also occurs when air remains in the pump chamber.

Further, when the vane is forcibly pushed out by the spring, there is a problem that the sliding resistance increases because the spring biasing force of the vane is constant at any rotational position. In particular, there is a problem that when the vane is pushed into the vane groove, the tip of the vane is strongly pressed against the inner peripheral surface of the pump chamber, and the sliding resistance increases.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and ensures that the operation of projecting the vane at the time of starting is performed without increasing the sliding resistance, thereby obtaining a desired oil discharge pressure in a short time. It is an object of the present invention to provide a balanced vane pump structure that can be used.

[0008]

In order to achieve the above object, the present invention provides a rotor having a vane fitted in a radially provided groove and a housing in which the rotor is rotatably incorporated. In a balanced vane pump structure in which a pump chamber having a substantially elliptical inner peripheral surface in which the outer diameter end of the vane slides and moves with the rotation of the vane is formed in the housing, the vane contacts the inner diameter side back of the vane, A cam mechanism is provided that pushes the vanes radially outward from the rotation axis of the rotor as the rotor rotates.

[0009] In the case of the parallel vane pump structure having such a configuration, when the rotor starts rotating at the time of starting the pump, the vane fitted into the rotor also rotates at the same time. With this rotation, the back of the vane slides against the cam mechanism and is pushed out. Thus, even when sufficient pressure cannot be supplied to the back of the vane when starting the equilibrium vane pump, the vane is reliably pushed out, and the oil projection pressure required for the equilibrium vane pump can be obtained in a short time and reliably. be able to.

Preferably, the cam mechanism is provided within a range in which the vane moves from the bottom dead center to the top dead center as the rotor rotates. When the vane moves while sliding on the peripheral surface of the pump chamber with the rotation of the rotor, the vane moves so as to be pushed up from the bottom dead center to the top dead center, and is pushed down from the top dead center to the bottom dead center. Go to In this case, the push-down movement from the top dead center to the bottom dead center is pushed down by abutting on the inner peripheral surface when the tip of the vane slides on the inner peripheral surface, so that the vane can be reliably moved without a cam mechanism. Is moved downward. For this reason, the cam mechanism
Its function is sufficient if it is provided within the range where the vane moves from the bottom dead center to the top dead center.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to FIGS. The balanced vane pump 1 mainly includes a housing 2 having a pump chamber 2A therein.
, A rotor 4 housed in the housing 2 and rotating about the rotating shaft 3, and a vane 5 provided on the outer periphery of the rotor 4 so as to be able to protrude and retract.

The housing 2 has a pump chamber 2A inside.
And a suction port 8 that closes one side (lower side in FIG. 2) of the main body 7 while rotatably supporting the rotating shaft 3 of the rotor 4 and sucks oil into the pump chamber 2A. One side lid 10 having a discharge port 9 for discharging oil from inside the pump chamber 2A, and the other side of the main body 7 being closed in a state where the rotating shaft 3 of the rotor 4 is rotatably supported, defines the pump chamber 2A. And the other-side lid 11. The main body 7 is a disk having a predetermined thickness, and has a pump chamber 2A having an elliptical inner peripheral surface 2B formed therein. The suction port 8 and the discharge port 9 of the one-side lid 10 are provided two by two facing the pump chamber 2A. The suction port 8 and the discharge port 9 are provided to face each other in the major axis direction of the elliptical shape of the pump chamber 2A (the vertical direction in FIG. 1). Thereby, pumping is performed on both long-side directions in the pump chamber 2A.

The rotor 4 includes one side lid 10 and the other side lid 1
1 is attached to a rotating shaft 3 rotatably supported by the rotating shaft 1 and is rotatably driven by the rotating shaft 3 while being housed in the housing 2. This rotor 4
It is formed in a thick disk shape, and radial vane grooves 15 are formed on its outer periphery at regular intervals. The base end of the vane groove 15 is enlarged, and this part is connected to the discharge port 9 so that a part of the discharge pressure is supplied. A substantially rectangular plate-like vane 5 is inserted into each vane groove 15 so as to be able to protrude and retract, and is urged in a direction to be pushed out from the rotor 4 by the discharge pressure supplied to the enlarged base end. A circular recess 4A is formed on the other lid 11 side of the rotor 4 to allow a guide plate 17 to be described later to be mounted.

A guide plate 17 as a cam mechanism is attached to the other side lid 11 side. The guide plate 17 is a cam mechanism that comes into contact with the back of the vane 5 and pushes the vane 5 radially outward from the rotation axis of the rotor 4 as the rotor 4 rotates. The guide plate 17 has an outer peripheral shape substantially similar to the inner peripheral surface shape of the pump chamber 2A of the housing 2. The dimensions of the guide plate 17 are such that the vanes 5 are not sandwiched between the outer periphery of the guide plate 17 and the inner periphery of the pump chamber 2A of the housing 2 and the minimum pushing amount that can close the suction port 8 It is set to be.

Next, the operation of the balanced vane pump 1 having the above configuration will be described. When the rotating shaft 3 rotates by starting the balanced vane pump 1, the rotor 4 rotates. Thus, the vane 5 rotates in the pump chamber 2A of the housing 2. During this start-up, the discharge pressure of the balanced vane pump 1 itself is low, so that it is not possible to supply a pressure sufficient to push the vane 5 out of the vane groove 15 of the rotor 4.

However, the vane 5 rotating together with the rotor 4
Since the base end thereof slides on the guide plate 17,
The guide 2 is pushed by the guide plate 17 to protrude and retract along the inner peripheral surface of the pump chamber 2A of the housing 2. Thereby, the space (the outer peripheral surface of the rotor 4, the two adjacent vanes 5, the inner peripheral surface of the pump chamber 2A, the one-side lid 10 and the other-side lid) The space defined by the inner surface of the body 11) is surely created. Then, by the rotation of the rotor 4, the oil is sucked from the suction port 8 while the space becomes large, and the oil is discharged from the discharge port 9 while the space becomes small. Part of the pressure of the discharged oil is also supplied to the vane groove 15, and the vane 5 is urged against the inner peripheral surface of the pump chamber 2A by a normal urging force.

As a result, the oil projection pressure required for the balanced vane pump 1 can be reliably obtained in a short time. As a result, the balanced vane pump 1 can be started in a short time and reliably even in a state where the viscosity of the oil is high in a cold region or the like or when air is mixed in the pump chamber 2A. Become.

Further, the guide plate 17 does not push the vane 5 to a state in which it comes into contact with the inner peripheral surface 2B of the pump chamber 2A, but only to a position immediately before the contact, due to its set dimensions. The vane 5 is the inner peripheral surface 2 of the pump chamber 2A.
In the state of contact with B, only the discharge pressure of the balanced vane pump 1 itself acts. As a result, the vane 5 is removed from the pump chamber 2
A is not pressed excessively against the inner peripheral surface of A, and the sliding resistance is not increased.

[0019]

[Modification] In the above embodiment, the guide plate 17 is formed in the same shape as the inner peripheral surface 2B of the pump chamber 2A. However, as shown in FIG. (Only within a range where vane 5 moves from bottom dead center to top dead center with rotation of 4) vane 5
The outer peripheral surface shape of the guide plate 17 may be set so as to contact the back of the vane and push the vane 5 radially outward from the rotation axis of the rotor 4 with the rotation of the rotor 4. As a result, when the rotor 4 rotates, the vane 5 is pushed out by the guide plate 17 at a position facing the suction port 8, and the oil is reliably sucked into the pump chamber 2A even when the balanced vane pump 1 is started. On the other hand, at the discharge port 9, the vane 5 is only pushed into the vane groove 15 while sliding on the inner peripheral surface of the pump chamber 2 </ b> A, so that the oil is reliably discharged from the discharge port 9. As a result, the oil projection pressure required for the balanced vane pump 1 can be reliably obtained in a short time.

In the above-described embodiment, the guide plate 17 is provided on the other lid 11 side, but may be provided on the one lid 10 without blocking the suction port 8 and the discharge port 9. With this configuration, the same operation and effect as those of the above embodiment can be obtained.

Further, the guide plate 17 is connected to the one-side lid 1.
It may be provided on the 0 side and the other side lid 11 side, respectively. In this case, since the vanes 5 are simultaneously pushed from above and below, the vanes 5 can be pushed more reliably.

[0022]

FIG. 4 shows an example of a belt-type continuously variable transmission using the vane pump having the above-described configuration. FIG. 5 shows an input-side component (a portion having a torque converter, a vane pump, a forward / reverse switching mechanism, etc.) A of the transmission, and FIG. 6 shows a V-belt type continuously variable transmission mechanism component B.
FIG. 7 shows a component C of the output side transmission gear portion and the final reduction mechanism.

This transmission employs a continuously variable transmission mechanism 34 that performs a shift according to a pulley ratio created by a metal belt 35, a drive pulley 36, and a driven pulley 37, so that the entire range from low speed to high speed is smooth and refreshing. This is an electronically controlled automatic transmission that balances driving and fuel economy.

Basically, the transmission is arranged in series with the engine output shaft, and the final reduction mechanism 40 is built in a space surrounded by the torque converter case 31 and the transmission cases 32 and 33. The torque converter 21 directly connected to the engine crankshaft has a starter gear and also serves as a flywheel mass. A lock-up clutch is built in the torque converter 21, and at the time of lock-up, engine power is transmitted directly to the transmission input shaft.

A pump driving gear is attached to a hub at the end of the torque converter, and the oil pump 1 (the vane pump according to the present invention) is constantly driven via a chain 22. The transmission input shaft spline-engaged with the turbine of the torque converter is spline-engaged with the planetary gear configuration of the planetary type forward / reverse switching mechanism 25. A forward clutch is spline-engaged on the input shaft side of the drive pulley 36.
Further, the reverse brake is arranged on the outer peripheral side of the planetary gear configuration. The final reduction mechanism 40 is driven via a power transmission gear train 45 driven by the driven pulley 37. The transmission is equipped with a total of three rotation sensors to constantly monitor the rotation of the gear.

The pump 1 sucks oil through a strainer built in an oil pan below the transmission. This suction oil passes through a suction oil passage formed in the lower part of the transmission case and in the valve body, and reaches the oil pump 1 through a joint pipe having a floating structure.
The oil pump 1 is attached to an oil passage mating surface of a torque converter case 31, and is driven by an engine from the torque converter 21 via a chain 22.

The oil sucked / discharged by the pump 1 passes through a torque converter case oil passage, and is used for a control oil pressure required for gear shifting, a torque converter system, lubrication, cooling, etc. through a hydraulic control circuit.

[0028]

As described above, in the balanced vane pump structure of the present invention, the vane comes into contact with the back of the vane,
A cam mechanism that pushes the vanes radially outward from the rotation axis of the rotor with the rotation of the rotor is provided, so that the oil viscosity is high in cold climates and the like and air is mixed in the housing. Even in this state, the desired hydraulic pressure can be generated by activating the balanced vane pump quickly and reliably. In addition, this cam mechanism does not push the vane to the state where it contacts the inner peripheral surface of the housing, but only to the position before the contact.Therefore, in the contact state, only the discharge pressure of the balanced vane pump itself acts. The sliding resistance can be reduced without excessively pressing the vane against the inner peripheral surface of the housing.

[Brief description of the drawings]

FIG. 1 is a front view schematically showing a balanced vane pump according to the present invention.

FIG. 2 is a schematic side sectional view of a balanced vane pump according to the present invention.

FIG. 3 is a front view showing a modification of the balanced vane pump according to the present invention.

FIG. 4 is a sectional view showing an example of a belt-type continuously variable transmission using the vane pump according to the present invention.

FIG. 5 is a cross-sectional view showing an input-side component (a portion having a torque converter, a vane pump, a forward / reverse switching mechanism, and the like) of the transmission.

FIG. 6 is a cross-sectional view showing components of a V-belt type continuously variable transmission mechanism in the transmission.

FIG. 7 is a sectional view showing components of an output side transmission gear portion and a final reduction mechanism in the transmission.

[Explanation of symbols]

 1: Balanced vane pump 2: Housing 2A: Pump chamber 4: Rotor 5: Vane 7: Main body 15: Vane groove

 ──────────────────────────────────────────────────の Continued on the front page (72) Inventor Kenji Yamane 1-4-1 Chuo, Wako-shi, Saitama

Claims (2)

[Claims] 1. A rotor in which a vane is fitted in a radially provided groove, and a housing in which the rotor is rotatably incorporated. The outer diameter end of the vane slides with the rotation of the rotor. In the balanced vane pump structure in which a pump chamber having a substantially elliptical inner peripheral surface is formed in the housing, the pump chamber comes into contact with the inner diameter side back of the vane, and the vane is rotated by the rotation of the rotor. An equilibrium vane pump structure comprising a cam mechanism for pushing radially outward from a rotation axis. 2. The balanced vane pump according to claim 1, wherein the cam mechanism is provided within a range in which the vane moves from bottom dead center to top dead center as the rotor rotates. Construction.