JP2001165064A - Oil pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent increase in a flow velocity of the hydraulic oil in an oil pump device. SOLUTION: In this oil pump, a means for controlling the change of a flow velocity of the hydraulic oil between a second port 321b and a third port 321c to the change of the capacity of a pump room defining the shape of an opening, is mounted on at least one of a side end part in the rotating direction of one of the second port 321b and the third port 321c, and a side end part in the anti-rotating direction of the other of the second port 321b and the third port 321c.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil pump device, and more particularly, to an oil pump which is rotationally driven by a drive source such as an engine whose rotational speed changes, and which recirculates a part of hydraulic oil discharged from the oil pump. The present invention relates to an oil pump device configured by a control valve capable of causing a predetermined amount of hydraulic oil to be supplied to a portion to be supplied.

[0002]

2. Description of the Related Art Japanese Patent Laying-Open No. 10-73084 (hereinafter referred to as a first prior art) discloses an oil pump device of this type.
And Japanese Patent Application Laid-Open No. 9-126153 (second prior art) are known. These devices have a plurality of external teeth, an inner rotor rotatably mounted in a pump housing and rotatably driven by a drive source such as an engine whose rotational speed changes, and the external teeth of the inner rotor. An oil pump having an outer rotor rotatably mounted in the pump housing, the oil pump having a plurality of internal teeth that define a plurality of pump chambers between the external teeth and the external teeth. And a control valve capable of circulating a part of the working oil.

[0003] In the first prior art oil pump device, a discharge port which is always in communication with a discharge port, a main suction port which is always in communication with a suction port, and which is in communication with and blocked by a main suction port through a control valve. The pump is configured as a single oil pump having a sub-suction port interrupted and communicated with the discharge port, and as shown in FIG. 15, a pump at the rotation-direction end of the inner rotor 222 of the sub-suction port 221d. The shape of the opening to the chamber and the main suction port 22
The opening shape of the inner rotor 222 in the counter rotation direction side of the inner rotor 222 into the pump chamber is set between the rotation direction side end of the main suction port 221c adjacent to the discharge port and the counter rotation direction end of the discharge port. It is defined so as to follow the shape of the pump chamber R1 having a smaller volume than the maximum volume of one pump chamber to be located. In FIG. 15, reference numeral 221 denotes a pump housing, and 223 denotes an outer rotor.

Further, in the second prior art oil pump device, as shown in FIG. 29, a suction port (not shown) communicating with a suction port (not shown) and a main discharge port 4 are provided.
21b, a pump chamber configured as a single oil pump 420 having a sub-discharge port 421c and having a smaller volume than the pump chamber having the maximum volume formed between the suction port and the main discharge port 421b. R1
The shape of the opening of the sub-discharge port 421c at the end in the non-rotational direction into the pump chamber R1 is defined so as to conform to the shape of (1). 29, reference numeral 421 denotes a pump housing, 423
Is an outer rotor.

[0005]

In the oil pump device based on the first prior art, a single oil pump having a suction port, a main suction port, a sub suction port, a discharge port, and a discharge port is provided. Since the control valve controls the flow of part of the hydraulic oil discharged from the oil pump to the main suction port and the sub suction port in accordance with the pressure of the hydraulic oil discharged from the oil pump, the oil is It is possible to make the pump device small, light and compact, improve the mountability of the oil pump device on a vehicle body or the like, secure a required oil amount according to the rotation speed of the drive source, and provide a pump. The load can be reduced. Further, in the above-described conventional apparatus, the shape of the opening at the ends of both suction ports adjacent to each other is
A pump chamber whose volume is smaller by a predetermined ratio than the maximum volume of one pump chamber located between the rotation-side end of the suction port adjacent to the discharge port and the counter-rotation-side end of the discharge port. By stipulating that it conforms to one shape of
Prevents instantaneous reduction of suction area during minute rotation,
Increase in suction flow rate due to instantaneous reduction of suction area
Cavitation is prevented from occurring due to a decrease in pressure in the pump chamber.

However, in the oil pump device according to the first prior art, the opening shapes of the ends (shutoff portions) of the suction ports described above are simply defined radially by defining the openings at both ends. Although it is possible to prevent the instantaneous reduction of the suction passage cross-sectional area of each suction port during the minute rotation, the rotation of the inner rotor and the outer rotor of the pump chamber defined so that the end of each suction port follows. As the pump chamber and the respective suction ports have a small suction passage cross-sectional area with respect to the change in volume caused by the pump oil, the suction of the hydraulic oil as shown in FIG. There is a problem that the flow velocity increases, cavitation occurs, and noise occurs. FIG.
In FIG. 4, point 0 is the rotational position shown in FIG.

[0007] In the oil pump device based on the second prior art, the suction port, the main discharge port,
A single oil pump having a sub-discharge port and a discharge port, and an operation discharged from the oil pump to return a part of hydraulic oil discharged from the main discharge port and the sub-discharge port of the oil pump to the suction port. The control valve is controlled in accordance with the oil pressure, and the opening shape of the sub-discharge port on the opposite side in the non-rotational direction is changed to the capacity of the pump chamber having the maximum volume formed between the suction port and the main discharge port. By defining the shape so as to conform to the shape of one pump chamber having a smaller volume, it is possible to prevent the discharge area from being reduced due to rotation, and to increase the discharge area instantaneously to thereby increase the discharge flow rate / pump chamber (FIG. 29). The pressure in R1) is reduced to prevent an increase in the driving horsepower of the pump.

However, in the oil pump device according to the first prior art, the opening shapes of the ends (shutoff portions) of the suction ports described above are simply defined in a radial shape by defining the opening shapes of both ends. Although it is possible to prevent the instantaneous reduction of the suction passage cross-sectional area of each suction port during the minute rotation, the rotation of the inner rotor and the outer rotor of the pump chamber defined so that the end of each suction port follows. As the pump chamber and the respective suction ports have a small suction passage cross-sectional area with respect to the change in volume caused by the pump oil, the suction of the hydraulic oil as shown in FIG. There is a problem that the flow velocity increases, cavitation occurs, and noise occurs. FIG.
In FIG. 4, point 0 is the rotational position shown in FIG.

Further, in the oil pump device according to the second prior art, the end portions (the cut-off portions) of the respective discharge ports described above.
Although the opening shape at both ends is simply defined radially by the definition of the opening shape of the above, it is possible to prevent the instantaneous discharge passage cross-sectional area of each discharge port from being reduced at the time of minute rotation. With respect to a change in volume due to rotation of the inner rotor and the outer rotor of the pump chamber defined so that the end of the discharge port is along the discharge chamber, the discharge chamber has a small cross-sectional area between the pump chamber and each discharge port. In the vicinity of the rotational position shown in FIG. 29, which is the volume of the oil, the discharge flow rate of the hydraulic oil (the pressure in the pump chamber R1 in FIG. 29) increases as shown in FIG. This causes problems such as increase in noise and generation of noise.

[0010] Therefore, an object of the present invention is to prevent cavitation caused by an increase in the flow rate of hydraulic oil, an increase in drive torque of a pump, and generation of noise in an oil pump device.

[0011]

Means for Solving the Problems The technical means taken to solve the above problem is a drive source having a plurality of external teeth, which is rotatably assembled in a pump housing and whose rotation speed changes. An inner rotor that is rotatably driven, and a plurality of inner teeth that mesh with outer teeth of the inner rotor and define a plurality of pump chambers between the outer teeth and are rotatably mounted in the pump housing. An outer rotor, first, second, and third ports formed in the pump housing and communicating with the pump chamber at different positions in a circumferential direction of the rotor; and positions between the first port and the second port. One pump chamber has the largest volume,
One of the second port and the third port, a first opening shape to a pump chamber at a rotation direction side end of the inner rotor, or the other of the second port and the third port of the inner The second opening shape to the pump chamber at the opposite rotation direction end of the rotor is defined so as to conform to the interdental shape of the rotor constituting the pump chamber located between the second port and the third port. An oil pump device configured to pump a predetermined amount of hydraulic oil to a portion to be supplied, the pump comprising: a pump means configured to control communication between the second port and the third port. And at least one of the rotation-side end at one of the third ports and the counter-rotation-side end at the other of the second port and the third port. Over DOO and the hydraulic oil between the third port is to provided a means for suppressing the variation of flow rate to volume change of the pump chamber that defines the opening shape.

In the above means, the suppressing means comprises:
The rotation-side end of one of the second port and the third port, or the counter-rotation-side end of the other of the second port and the third port is the second end.
A second port and the third port, the second port and the third port are extended toward one of the second port and the third port. The second port and the third port may be communicated with each other through the second port, and the suppressing means may be configured to include one of the second port and the third port in the rotation direction side end or the second port. And the other one of the second port and the third port, the other one of the second port and the third port, or the second port and the third port. Preferably, the communication groove is formed to extend toward the other end in the rotation direction.

[0013]

According to the present invention, the end of the inner rotor in the rotation direction at one of the second port and the third port and the inner rotor at the other of the second port and the third port. The suppression means provided on at least one of the opposite ends in the anti-rotational direction makes the pump chamber defining the opening shape at both ends and the pump oil defining the opening shape of the hydraulic oil between the second port and the third port. It is possible to suppress a change in the flow velocity with respect to a change in the volume. As a result, it is possible to prevent the flow rate of the hydraulic oil from increasing near the rotational position where the pump chamber has a predetermined volume, to suppress the occurrence of cavitation and an increase in the oil pressure in the pump chamber, and to reduce the quietness of the oil pump device. , And it is possible to prevent the drive torque from increasing.

[0014] The restraining means may be connected to one end of the second port and the third port in the rotational direction or the other end of the second port and the third port in the anti-rotation direction. The third port extends toward the other end in the anti-rotational direction or the other end of one of the second port and the third port, and extends through the pump chamber to the second port and the third port. The second port and the third port may be formed with the port in communication with each other, or the second port and the third port may be formed with the second port and the third port in the opposite direction. The communication groove formed extending toward the other end of the second port and the third port in the opposite rotation direction or the other end of the second port and the third port in the rotation direction can be easily formed. Can be configured.

Further, when the suppressing means is constituted by a communication groove, the cross-sectional area of the passage can be arbitrarily changed by changing the depth, length, width, etc. of the groove, so that the flow rate of the hydraulic oil can be easily changed. And the second port or the third port
When the port communicates with the first port via the control valve, the flow of hydraulic oil between the second port and the third port via the pump chamber can be suppressed, and the efficiency of the oil pump device decreases. Can be prevented.

The communication between the second port and the third port is periodically generated by the rotation of the inner rotor, and the pressure of the hydraulic oil between the second port and the third port periodically changes (pulsates). . This periodic change in pressure (pulsation) generates noise. However, by forming the communication groove into a throttle shape (orifice shape) that prevents transmission of pressure (pulsation) like a narrow groove or a thin groove, the pressure is reduced. Generation of periodic changes (pulsations) can be reduced, and noise can be prevented.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. The oil pump device shown in FIG. 1 is a crankshaft 1 of a vehicle engine (internal combustion engine).
The oil pump 20 includes a control valve (control means) 30 capable of returning a part of the hydraulic oil discharged from the oil pump 20 to the suction side. The hydraulic oil discharged from the oil pump 20 is supplied through a discharge path 41 to a portion to be supplied, that is, a hydraulically operated actuator of a variable valve operating device in an engine, a lubricated portion such as a bearing in an engine, and a cylinder or piston. , Etc., respectively. In addition, it is configured that the working oil is returned from the supplied part 50 to the oil pan 40 of the engine through the discharge path 42.

The oil pump 20 includes the crankshaft 1
0, the pump housing 21 is rotatably driven in the counterclockwise direction in FIG. 1, and an inner rotor 22 rotatably mounted in the pump housing 21 and rotatably driven by the crankshaft 10. An outer rotor 23 which is rotatably assembled in the pump housing 21 with a predetermined amount of eccentricity with respect to the inner rotor 22 and is rotated in the same direction by the inner rotor 22 with the inner teeth 23a meshing with the outer teeth 22a of the inner rotor 22.
It has. The outer teeth 22a and the inner teeth 23a are defined by a trochoid curve or a cycloid curve.

The pump housing 21 has a suction port 21a connected to the suction path 43 and communicating with the oil pan 40, a discharge port 21b connected to the discharge path 41, and a main suction port (first port) constantly communicating with the suction port 21a. 2 ports) 21c
And a sub suction port (third port) 21d which is communicated with and blocked from the main suction port 21c via the control valve 30.
And a discharge port (first port) 21e which is always in communication with the discharge port 21b.
1e does not communicate with each other via the pump chambers R formed between the external teeth 22a and the internal teeth 23a. Also,
The main suction port 21c is located on the rotation direction side (counterclockwise side in FIG. 1) of the oil pump 20 with respect to the sub suction port 21d. As shown in FIGS. 1 and 10,
The shape of the opening of the sub suction port 21d at the rotation direction end of the inner rotor 22 into the pump chamber R and the shape of the opening of the main suction port 21c at the opposite rotation direction end of the inner rotor 22 into the pump chamber R are determined by discharge. The end of the main suction port 21c adjacent to the port 21e in the rotation direction and the discharge port 21
It is defined so as to conform to the shape of the pump chamber R1 having a volume smaller by a predetermined ratio than the maximum volume of one pump chamber R located between the pump chamber R and the end portion on the anti-rotation side. FIG.
0 is an enlarged view of the state where the cover 24 of the A section in FIG. 1 is removed, and shows a state where the pump chamber R1 has a predetermined volume at the rotational position of the inner rotor 22 and the outer rotor 23, and the predetermined volume is the main volume. It is set arbitrarily according to the desired amount of hydraulic oil to be distributed between the suction port 21c and the sub suction port 21d.

Further, in the first embodiment, FIG.
As shown in FIG. 11, a communication groove formed of a thin groove toward the rotation-side end of the sub-suction port 21d at the end of the main suction port 21c in the anti-rotation direction of the inner rotor 22 (suppression means). 21) is formed to extend. In addition, the communication groove 21g is provided with both suction ports 21.
g, 21c, a partition 2 of the pump housing 21
1f is formed on the end face on the pump chamber R1 side.

As shown in detail in FIGS. 2 and 3, the control valve 30 has an inner hole 31a.
A valve housing 31 having a control port 31b, a sub port 31c, and a main port 31d communicating with the valve housing 1a, respectively, and the valve housing 31 is slidably mounted in the inner hole 31a of the valve housing 31 in the axial direction and flows through the control port 31b. Oil pressure (discharge pressure of oil pump 20)
At one end (upper end in the figure), and the variable throttle portions A and B are formed by the valve housing 31.
A spool 32 for variably controlling the communication and blocking between the b, 31c and 31d by a land portion 32a and a spring 33 for urging the spool 32 upward in FIG. The sub port 31c is always in communication with the sub suction port 21d of the oil pump 20, and the main port 31d is always in communication with the main suction port 21c of the oil pump 20. The chamber of the spring 33 is always in communication with the oil pan 40, and is configured so that no pressure (force for pushing the spool 32 upward in the drawing) is generated.

As shown in detail in FIG. 3, the land 32a of the spool 32 is single and is formed at one end (upper end in the drawing) of the spool 32. On the other end side of the land portion 32a receiving the pressure of the hydraulic oil flowing from the control port 31b to the main port 31c in the third control mode, a slope surface inclined from the outer peripheral portion of the land portion 32a toward the axis of the spool 32 is provided. (Tapered surface) 32b is formed. Also, slope surface 3
A radial step 32c is formed between the land-side end of 2b and the outer periphery of the land 32a.

In the control valve 30, the control port 3
The first control mode (see FIG. 5) in which the sub port 31c communicates only with the main port 31d in accordance with the hydraulic pressure (discharge pressure) applied to the sub port 31c, and the sub port 31c maintaining the communication between the sub port 31c and the main port 31d And the control port 31b are communicated with each other through the variable throttle unit A, and the main port 31d and the control port 31 are connected to the sub port 31c.
b in the second control mode (FIG. 6).
) And the sub port 31c and the main port 31 while the communication between the sub port 31c and the control port 31b is maintained.
d through the variable throttle section B to make the control port 31b
A third control mode (see FIG. 7) in which hydraulic fluid flows from the first to the sub port 31c and the main port 31d, and a fourth control mode in which the sub port 31c communicates only with the control port 31b.
In the control mode (see FIG. 8), the sub port 31c is communicated with the main port 31d while maintaining the communication between the sub port 31c and the control port 31b, so that the hydraulic oil flows from the control port 31b to the sub port 31c and the main port 31d. The control can be performed in the fifth control mode (see FIG. 9), whereby the discharge amount characteristics shown in FIG. 4 can be obtained. In the first control mode, the characteristics between points 0 and a in FIG. 4 are obtained, in the second control mode, the characteristics between points a and b in FIG. 4 are obtained, and in the third control mode, b in FIG. The characteristics between the points c and c are obtained, the characteristics between the points c and d in FIG. 4 are obtained in the fourth control mode, and the characteristics after the point d in FIG. 4 are obtained in the fifth control mode.

In the first embodiment configured as described above, when the rotation speed N of the crankshaft 10 is in the rotation range between 0 and N1, the spool 32 of the control valve 30 is schematically shown in FIG. In the position shown, the communication of the sub port 31c with the control port 31b is interrupted and the communication with the main port 31d is maintained. For this reason, in the oil pump 20, since both the main suction port 21c and the sub suction port 21d function sufficiently as a suction port, the hydraulic oil is sufficiently sucked from the main suction port 21c and the sub suction port 21d, and in the low rotation region. 4 is obtained, the discharge amount characteristic between points 0 and a shown in FIG. 4 is obtained, and the discharge amount is pressure-fed to the supply destination section 50 through the discharge path 41.

At this time, since the main suction port 21c is located on the rotation direction side of the oil pump 20 with respect to the sub suction port 21d, the sub suction port 21d is connected to the suction port 21a (main suction port) via the control valve 30. 21
Even if the pump chamber R communicated with the sub-suction port 21d is not sufficiently sucked into the pump chamber R due to the pressure loss due to the communication with c) and a negative pressure is generated in the pump chamber R, When the pump chamber R in which the negative pressure is generated communicates with the main suction port 21c as the oil pump 20 rotates, the negative pressure causes the operating oil to flow into the main suction port 21c.
The suction pressure is sucked into the pump chamber R from c, and the negative pressure disappears. As a result, the required oil amount in the low rotation region can be secured.

When the rotation speed N of the crankshaft 10 is in the rotation range between N1 and N2, the spool 32 of the control valve 30 is at the position schematically shown in FIG. In a state where the communication with the port 31d is maintained (the state where the communication with the control port 31b is hardly stopped), the amount of communication with the control port 31b is variably controlled by the variable throttle A, and the sub port 31c is connected to the main port. Hydraulic oil flows from 31d and the control port 31b.
Therefore, in the oil pump 20, a part of the hydraulic oil flowing from the discharge port 21e to the discharge port 21b flows into the sub suction port 21d through the control valve 30, and the hydraulic oil flows from the main suction port 21c to the sub suction port 21d. Is sucked, and the main suction port 21c functions sufficiently as a suction port, but the function of the sub suction port 21d as the suction port is reduced according to the flow rate of the hydraulic oil flowing from the control port 31b through the variable throttle portion A. Therefore, the discharge amount characteristic between points a and b shown in FIG. 4 can be obtained, and the discharge amount corresponding to the reduced function of the sub suction port 21d as the suction port can be reduced, and the pump load can be reduced. .

When the rotation speed N of the crankshaft 10 is in the rotation range between N2 and N3, the spool 32 of the control valve 30 is in the position schematically shown in FIG. The amount of communication with the main port 31d is variably controlled by the variable throttle unit B in a state where communication with the port 31b is maintained (in a state where the throttle is almost not throttled by the variable throttle unit A). And the working oil flows to the main port 31d. For this reason, in the oil pump 20, a part of the hydraulic oil flowing from the discharge port 21e to the discharge port 21b flows into the sub suction port 21d and the main suction port 21c via the control valve 30, and the sub suction port 21d is connected to the suction port. The function of the main suction port 21c as the suction port can be reduced in accordance with the flow rate of the hydraulic oil flowing from the control port 31b through the variable throttle portion B in a state where the main suction port 21c hardly functions. A point discharge amount characteristic is obtained, and the discharge amount corresponding to the sub suction port 21d not functioning as the suction port and the discharge amount corresponding to the deterioration of the function of the main suction port 21c as the suction port can be reduced to reduce the pump load. Can be planned.

When the rotation speed N of the crankshaft 10 is in the rotation range between N3 and N4, the spool 32 of the control valve 30 is at the position schematically shown in FIG. While the communication with the port 31b is maintained and the communication with the main port 31d is shut off, the hydraulic oil flows from the control port 31b to the sub port 31c, but the hydraulic oil flows from the control port 31b to the main port 31d. Not flowing. Therefore, in the oil pump 20, a part of the hydraulic oil flowing from the discharge port 21e to the discharge port 21b flows into the sub-suction port 21d via the control valve 30, but does not flow into the main suction port 21c. In the state where 21d hardly functions as a suction port, the main suction port 2
Since 1c functions sufficiently as a suction port, the discharge amount characteristic between the points c and d shown in FIG. 4 is obtained, and the discharge amount can be reduced by the amount that the sub suction port 21d does not function as the suction port. The load can be reduced.

When the rotational speed N of the crankshaft 10 is in the rotational range of N4 or more, the spool 32 of the control valve 30 is located, for example, in the position schematically shown in FIG. Is fully open, the amount of communication between the main port 31d and the control port 31b and the sub port 31c is variably controlled, and hydraulic oil flows from the control port 31b to the sub port 31c and the main port 31d. For this reason, in the oil pump 20, part of the hydraulic oil flowing from the discharge port 21 e to the discharge port 21 b is supplied to the sub suction port 21 through the control valve 30.
d and the main suction port 21c, and the sub suction port 21d hardly functions as a suction port.
Since the function of the main suction port 21c as the suction port is reduced according to the flow rate of the hydraulic oil flowing from the control port 31b, the discharge amount characteristic after the point d shown in FIG. The discharge amount not functioning as a port and the discharge amount corresponding to the function deterioration of the main suction port 21c as a suction port can be reduced, and the pump load can be reduced.

Next, a second embodiment shown in FIG. 16 will be described.

As shown in FIG. 16, the oil pump device
The vehicle includes an oil pump 320 that is rotationally driven by a crankshaft (drive source) 310 of a vehicle engine, and a control valve (control means) 330 that can recirculate a part of hydraulic oil discharged from the oil pump 320 to a suction side. And
Hydraulic oil discharged from the oil pump 320 passes through a supply oil passage 341 to be supplied 350, that is, a hydraulically operated actuator of a variable valve operating device in an engine, a lubricated portion such as a bearing in an engine, and a cylinder or a piston. Are configured to be pressure-fed to respective oil cooling portions and the like. It should be noted that the delivery path 350 is
2 so that the working oil is returned to the oil pan 340 of the engine.

The oil pump 320 is driven to rotate clockwise in FIG. 16 by a crankshaft 310. The oil pump 320 is rotatably mounted in the pump housing 321 by the crankshaft 310. An inner rotor 322 that is rotationally driven and a plurality of inner teeth 323a that are rotatably assembled in the pump housing 321 with a predetermined amount of eccentricity with respect to the inner rotor 322 and mesh with a plurality of outer teeth 322a of the inner rotor 322. An outer rotor 323 rotated in the same direction by the rotor 322 is provided. The external teeth 322a and the internal teeth 323a are defined by, for example, a trochoid curve or a cycloid curve.

External teeth 322a of the inner rotor 322;
A pump chamber R is formed between the outer rotor 323 and the internal teeth 323a. Since the outer rotor 323 is eccentric with respect to the inner rotor 322 by a predetermined amount, the arrangement of the pump chamber R is eccentric.

The pump housing 321 has a suction port (first port) 321a communicating with the oil pan 340.
And a main discharge port (second port) 321b communicating with the oil supply passage 341 via the main discharge passage 341a, and a sub discharge port (the second discharge port) communicating with the sub inflow port 331b of the control valve 330 via the sub discharge passage 341b. 3 ports) 3
21c are provided in the pump chamber R at different positions in the circumferential direction of the rotor. As described above, the pump chamber has the suction port 321a and the main discharge port 3
21b, a main pump chamber R2 is formed between the main discharge port 321b and the sub discharge port 321c. The main discharge port 321b is located upstream of the sub-discharge port 321c in the direction of arrow X in FIG. 16, and both ports do not communicate with each other in the circumferential direction, and thus have independent discharge functions and discharge characteristics.

As shown in FIG. 18, the sub discharge port 32
The opening shape of the end 1c of the inner rotor 322 on the opposite side in the rotation direction to the pump chamber R3 is defined so as to conform to the shape formed between the teeth of the inner rotor 322 and the outer rotor 323. The pump chamber R3 has a smaller inter-tooth shape (pump chamber) of the rotor formed between the suction port 321a and the main discharge port 321b than the capacity of the largest pump chamber (not shown).

FIG. 18 is an enlarged view of the actual oil pump shown in FIG. 16 and shows a state in which the pump chamber R3 has a predetermined volume at the rotational position of the inner rotor 322 and the outer rotor 323, and has a predetermined volume. Is set arbitrarily.

As shown in FIG.
A communication groove (suppression means) 32 formed of a thin groove toward the non-rotational side end of the inner rotor 322 of the main discharge port 321b at the non-rotational side end of the inner rotor 322 of FIG.
1 g is formed to extend.

As shown in FIG. 19, the communication groove 321g
Are formed on the pump chamber side end surface of the partition 321f of the pump housing 321 that partitions the two discharge ports.

The communication groove 321g allows the oil discharged by the pump chamber R3 to be supplied to the sub discharge port 321 by rotating the inner rotor 322 between the teeth of the pump chamber R3.
The sub-discharge port 321c and the pump chamber R3 communicate with each other before the opening shape of the sub-c port coincides with the opening shape of the sub-c port (the pump chamber R3 and the sub-discharge port 321c communicate with each other).

As shown in FIG. 25, the end of the main discharge port 321b in the rotation direction is connected to the inner rotor 322.
When the sub-discharge port 321c and the pump chamber R3 communicate with each other by the opening shape of the sub-discharge port 321c on the opposite rotation direction end to the pump chamber R3, the pump chamber R3 and the main discharge port 321c communicate with each other. By forming the main discharge port 321b and the port 321b so as to communicate with each other by the shape of the opening of the main discharge port 321b to the pump chamber R3, it is also possible to constitute the suppression means.

The control valve 330 has an inner hole 330a as shown in detail in FIG.
A valve housing 331 having a main inflow port 331a, a sub inflow port 331b, a merging port 331c, a first return port 331d, and a second return port 331e communicating with the valve housing 331, and an inner hole 330a in the valve housing 331 slides axially. At one end (upper end in the drawing), the pressure (discharge pressure of the oil pump) of the working oil flowing through the main inflow port 331a is movably assembled, and the variable throttle portion C,
D and E are formed, and communication between each port and blocking
A spool 332 variably controlled by 32a and 332b;
The spool 332 is constituted by a spring 333 for urging the spool 332 upward in FIG.
31a, the main discharge path 341a of the oil pump 320
At all times, at the sub-inflow port 331b at all times with the sub-discharge path 341b of the oil pump 320, and at the junction port 331c at the oil supply path 341 (the main discharge path 341b).
a), the first and second return ports 331d, 331d,
At 31e, it is always in communication with the oil pan 340 (suction port 343).

The land portions 332a, 33 of the spool 332
2b, as shown in detail in FIG.
2 are formed at one end side (upper end side in the figure) and the other end side (lower end side in the figure), and are operated in the state of FIG. Land part 33 which receives oil pressure
2a and one end of the land portion 332b, the outer periphery of the land portions 332a and 332b
Surface (tapered surface) 332 inclined toward the axis of
c, 332d are formed respectively. A radial step 332e is formed between the end of the slope surface 332c on one end side of the land portion 332a and the outer periphery of the land portion 332a.

In the control valve 330, the sub-inflow port 331b and the junction port 331c communicate with each other through the inner hole 330a in accordance with the hydraulic pressure (discharge pressure) applied to the main inflow port 331a. Port 331a and first and second return ports 331d, 331
e between the main discharge port 321b (main discharge path 341a) and the sub discharge port 3
The first control mode in which the hydraulic oil is discharged through both of the main discharge port 21c (the sub discharge passage 341b) and the communication between the main inflow port 331a and the inner hole 330a is cut off.
Hydraulic oil discharged from 1b flows into the oil supply passage 341, while the inner hole 330a and the second return port 331e communicate with each other by a predetermined amount, and the sub-inflow port 3 through the inner hole 330a.
31b is connected to the second return port 331e and the merge port 331c.
The hydraulic oil discharged from the sub-discharge port 321c by communicating with both of them is joined to the merge port 331c (the oil supply path 341).
And a second control mode in which a part of the hydraulic oil discharged from the sub-discharge port 321c is returned to the suction side by flowing to the second return port 331e (suction port 343). The communication with the hole 330a is shut off, and the hydraulic oil discharged from the main discharge port 321b flows into the oil supply passage 341 while the sub-inflow port 33
A third control mode in which the hydraulic fluid 1b and the second return port 331e are communicated through the inner hole 330a and most of the hydraulic oil discharged from the sub discharge port 321c is returned to the suction port 343 via the second return port 331e; The main inflow port 331 a and the first return port 331 d are
a and the sub-inflow port 331b
And the second return port 331e are communicated through the inner hole 330a, and a part of the hydraulic oil discharged from the main discharge port 321b and most of the hydraulic oil discharged from the sub discharge port 321c are returned to the suction port 343. The control can be performed in four control modes, whereby the ejection characteristics shown in FIG. 20 can be obtained. 20 in the first control mode, between points a and b in FIG. 20 in the second control mode, and between points b and c in FIG. 20 in the third control mode. In the fourth control mode, FIG.
The ejection characteristics shown below are obtained above the point c.

In the above-described second embodiment, when the rotation speed N of the crankshaft 310 is in a rotation range between 0 and N1, the spool 332 of the control valve 330 is moved to, for example, the position schematically shown in FIG. Accordingly, the main inflow port 331a is cut off from the communication with the inner hole 330a, and the sub inflow port 331b is connected to the junction port 331c via the inner hole 330a in the control valve 330.
For this reason, in the oil pump 320, both the main discharge port 321b and the sub discharge port 321c function sufficiently as discharge ports.
20b and the sub-discharge port 321c can be sufficiently discharged to secure a required oil amount in a low rotation region.
Is obtained, and the discharge amount is pressure-fed to the feed portion 350 via the oil supply passage 341.

The rotation speed N of the crankshaft 310
Is in the rotation range between N1 and N2, the spool 332 in the control valve 330 is, for example, at the position schematically shown in FIG. 22, and the sub-inflow port 331b has the inner hole 330a.
Is connected to the second return port 331e by a predetermined amount in a state where the communication with the junction port 332c is maintained. On the other hand, communication between the main inflow port 331a and the inner hole 330a is shut off. The amount of communication between the sub-inflow port 331b and the merge port 331c is controlled by the variable throttle portion D constituted by the land portion 332a.
The communication amount between the second return port 331e and the land portion 332
b is variably controlled by a variable aperture unit E constituted by b. Therefore, in the oil pump 320, the main discharge port 321b functions sufficiently as a discharge port, but the sub discharge port 321c is connected to the second return port 331.
In order to reduce the function as the discharge port in accordance with the flow rate of the hydraulic oil flowing from e through the variable throttle portion E, the discharge amount characteristic between the points a and b shown in FIG. 20 is obtained, and the discharge of the sub discharge port 321c is obtained. It is possible to reduce the driving force corresponding to the reduced function as the port, and to reduce the pump load.

The rotation speed N of the crankshaft 310
Is in the rotation range between N2 and N3, the spool 332 in the control valve 330 is, for example, at the position schematically shown in FIG. 23, and the sub-inflow port 331b is
31c, and the second through the inner hole 330a.
While the communication is made only with the return port 331e, the cutoff of the communication between the main inflow port 331a and the inner hole 330 is maintained. For this reason, in the oil pump 320, most of the hydraulic oil discharged from the sub-discharge port 321c is controlled by the control valve 330.
Flows into the second return port 331c through the sub-discharge port 321c so as to hardly function as a discharge port, and the flow rate of the hydraulic oil discharged from the main discharge port 321b becomes the discharge amount. Point b to c
The point discharge amount characteristic is obtained, and the discharge amount and the pump load can be reduced because the sub-discharge port 321c does not function as the discharge port.

The rotation speed N of the crankshaft 310
Is in the rotation range of N3 or more, the spool 332 is in the position schematically shown in FIG. 24 in the control valve 330, and the sub-inflow port 331b and the second return port 3
The main inflow port 331a and the first return port 331 are maintained in a state where the communication with the first inflow port 331a through the inner hole 330a is maintained.
The variable aperture section C communicates with the section d. For this reason, in the oil pump 320, the main discharge port 321
b flows into the first return port 331d via the control valve 330, while a part of the hydraulic oil flowing from the b through the main discharge path 341a to the oil supply path 341 and the sub discharge port 321
c communicates with the second return oil passage 331e, and the sub discharge port 321c hardly functions as a discharge port. This reduces the function of the main discharge port 321b as a discharge port in accordance with the flow rate of hydraulic oil flowing from the main inflow port 331a through the variable throttle portion D, out of the hydraulic oil discharged from the main discharge port 321b. The discharge amount characteristic shown in the region above the point c in FIG. 20 is obtained, and the discharge amount for the sub discharge port 321c not functioning as the discharge port and the main discharge port 321b
, The discharge amount can be reduced by the amount of deterioration of the function as the discharge port, and the pump load can be reduced.

As is apparent from the above description, in the first embodiment, in the second control mode of the control valve 30, the discharge amount can be reduced by the function of the sub suction port 21d as the suction port, which is reduced. In the third control mode of the control valve 30, the discharge amount by which the sub suction port 21d does not function as the suction port and the discharge amount by the function deterioration of the main suction port 21c as the suction port can be reduced.
In the fourth control mode, the discharge amount corresponding to the sub suction port 21d not functioning as the suction port can be reduced, and the discharge amount corresponding to the sub suction port 21d not functioning as the suction port in the fifth control mode of the control valve 30 can be reduced. In addition, the discharge amount of the function of the main suction port 21c as a suction port can be reduced, thereby reducing the pump load when the drive source shifts from the low rotation region to the middle / high rotation region and in the middle / high rotation region. Can be maximized, and the reduction of the driving power can be maximized.

In the first embodiment, the oil pump device is connected to the suction port 21 as shown in FIG.
a, main suction port 21c, sub suction port 21d,
A single oil pump 20 having a discharge port 21b and a discharge port 21e, and a part of hydraulic oil discharged from the oil pump 20 is discharged from the oil pump 20 to the main suction port 21c and the sub suction port 21d. Since the oil pump device is constituted by the control valve 30 which controls the oil pump device according to the pressure of the hydraulic oil, the oil pump device can be made small, light and compact, and the oil pump device can be mounted on a vehicle body or the like. Can be improved.

In the first embodiment, the shape of the opening of the sub suction port 21d at the rotation direction end of the inner rotor 22 into the pump chamber R1 and the main suction port 21c
Pump chamber R at the end of the inner rotor 22 in the anti-rotational direction.
1 is defined to conform to the shape of the pump chamber R1 (see FIG. 10).
A communication groove 21g extending toward the rotation-side end of the sub-suction port 21d of the sub-suction port 21d is formed at the end of the inner rotor 22 on the side opposite to the rotation direction. Therefore, the rotation of the inner rotor 22 and the outer rotor 23 causes the pump chamber R1 to move the end of the main suction port 21c on the opposite side to the rotation direction of the inner rotor 22 and the sub suction port 2c.
When passing through the end of the inner rotor 21 of the inner rotor 21 in the rotation direction, the suction passage cross-sectional area between the pump chamber R1 and each of the suction ports 21c and 21d becomes smaller with respect to the volume change of the pump chamber R1. This is prevented by the groove 21g (when the sectional area of the suction passage between the sub-suction port 21d and the pump chamber R1 decreases, the sectional area of the suction passage between the pump chamber R1 and the main suction passage 21c increases due to the communication groove 21g). As a result, an increase in the suction flow velocity of the hydraulic oil near the rotation position shown in FIG. 10 where the pump chamber R1 has a predetermined volume as shown in FIG. 14 is suppressed, and cavitation occurs due to the increase in the suction flow velocity, and noise is generated. This is prevented from occurring. In FIG. 14, the zero point is the rotation position shown in FIG. At this time, as described above, the discharge oil may be supplied to the sub suction port 21d via the control valve 30. However, since the communication groove 21g is formed by a thin groove, both the oils are supplied via the pump chamber R1. Suction ports 21c, 21d
It is possible to suppress the flow of hydraulic oil between the oil pumps, and to prevent the efficiency of the oil pump device from decreasing.

In the first embodiment, the communication groove 21g is formed by a thin groove having a uniform depth.
As shown in (1), the communication groove 21h may be constituted by an inclined groove whose depth increases with the rotation of the rotor, and the sectional area of the suction passage may gradually increase with the rotation of the rotor.
Further, as shown in FIG. 13, the communication groove is formed in a narrow groove extending toward the rotation-direction end of the sub-suction port 121d at the rotation-side end of the inner rotor 22 of the main suction port 121c. It can also be constituted by 121i (the depth of the narrow groove 121i may be uniform or inclined as shown in FIGS. 11 and 12). As described above, the communication groove can arbitrarily change the suction passage cross-sectional area by changing the depth, length, width, and the like of the groove, and can easily suppress a change in the suction flow rate of the hydraulic oil.

Further, in the second embodiment, in the second control mode of the control valve 330, the discharge amount corresponding to the reduced function of the sub-discharge port 321c as the discharge port can be reduced. Sub-discharge port 3 in mode
In the fourth control mode of the control valve 330, the discharge amount of the sub-discharge port 321c not functioning as the discharge port and the discharge amount of the main discharge port 321b can be reduced. The drive power can be reduced as much as possible, and the pump load can be reduced to the maximum when shifting from the low rotation range of the drive source to the middle / high rotation range and in the middle / high rotation range. Reduction can be maximized.

In the second embodiment, as shown in FIG. 16, the oil pump device includes a main discharge passage 341a, a sub discharge passage 341b, an oil supply passage 341, a suction passage 323, and a main discharge port 321b. , A single oil pump 320 having a sub-discharge port 321c and a suction port 321a, and a part of the flow of the hydraulic oil discharged from the oil pump 320 according to the pressure of the hydraulic oil discharged from the oil pump 320. Main discharge port 321b
And a control valve 330 for controlling the communication between the first and second return passages 331d and 331e and the main discharge passage 341a and the sub discharge passage 341b so as to recirculate the water from the sub discharge port 321c to the suction passage 323. For,
The oil pump device can be made small, light, and compact, and the mountability of the oil pump device on a vehicle body or the like can be improved.

In the second embodiment, the shape of the opening of the sub-discharge port 321c at the end of the inner rotor 322 in the anti-rotational direction to the pump chamber R3 is defined so as to conform to the shape of the pump chamber R3 (FIG. 18), the inner rotor 3 of the main discharge port 321c is provided at the end of the sub-discharge port 321c on the anti-rotation side of the inner rotor 322.
A communication groove 321g extending toward the end in the rotation direction of 22 is formed. Further, an opening shape to the pump chamber R3 is formed so that an end of the main discharge port 321b in the rotation direction of the inner rotor 322 is directed toward an end of the sub-discharge port 321c in the anti-rotation direction of the inner rotor 322. I have. Therefore, the rotation of the inner rotor 322 and the outer rotor 323 causes the pump chamber R3 to pass through the rotation-side end of the main discharge port 321b in the rotation direction of the inner rotor 322 and the sub-discharge port 321c in the direction opposite to the rotation of the inner rotor 322. At this time, the pump chamber R3 and each of the discharge ports 321b, 32
1c is prevented by the opening shape or the communication groove 321g. (If the cross-sectional area of the discharge passage between the main discharge port 321b and the pump chamber R3 is reduced, the pump is formed by the communication groove 321g. The cross-sectional area of the discharge passage between the chamber R3 and the sub-discharge port 321c increases, or the pump chamber R3 and the main discharge port 321
b). As a result, FIG.
As shown in FIG. 18, the increase in the discharge flow rate of the hydraulic oil near the rotation position shown in FIG. 18 where the pump chamber R3 has a predetermined volume (the pressure in the pump chamber between teeth increases) is suppressed, and the drive torque is reduced. The increase and the generation of noise are prevented.
In FIG. 28, the point 0 is the rotation position shown in FIG. At this time, as described above, the main discharge port 32
The discharge oil may be supplied (backflow) to the first port 1a through the communication groove 321g. However, since the communication groove 321g is formed by a thin groove, the two discharge ports 32 through the pump chamber R3 are provided.
The flow of hydraulic oil between 1b and 321c can be suppressed, and the efficiency of the oil pump device can be reduced, and the transmission of periodic pressure fluctuation (pulsation) of the discharge oil can be prevented.

In the above embodiment, the communication groove 321g is formed by a thin groove having a uniform depth. However, as shown in FIG. 26, the communication groove 321g is formed by an inclined groove whose depth increases with the rotation of the rotor. The groove 321h may be configured so that the suction passage cross-sectional area gradually increases as the rotor rotates.
Further, as shown in FIG. 27, the communication groove has a small groove extending toward the rotation-side end of the inner discharge port 321b of the main discharge port 321b toward the counter-rotation-side end of the inner rotor 322 of the sub discharge port 321c. 321i (the depth of the narrow groove 321i is shown in FIGS. 18 and 2).
6, or may be inclined).
As described above, the communication groove can arbitrarily change the cross-sectional area of the discharge passage by changing the depth, length, width, and the like of the groove, and can easily suppress a change in the discharge flow rate of the hydraulic oil.

In the above embodiment, the present invention is applied to the oil pump device driven by the crankshafts 10 and 310 of the vehicle engine (internal combustion engine).
The present invention can be applied to an oil pump device used for industrial equipment other than a vehicle in the same manner or with appropriate modifications, and the type of the oil pump (trochoid type in the above embodiment) and the driving form (the above embodiment) In this case, the direct drive type can be changed as appropriate.

[Brief description of the drawings]

FIG. 1 is a diagram showing a first embodiment of an oil pump device according to the present invention.

FIG. 2 is a detailed sectional view of the control valve shown in FIG.

FIG. 3 is an enlarged sectional view of a main part of the control valve shown in FIG. 2;

4 is a characteristic diagram showing a relationship between a rotation speed and a discharge amount obtained by the oil pump device shown in FIG.

FIG. 5 is a cross-sectional view schematically showing an operation of the control valve shown in FIGS. 2 and 3 in a first control mode.

FIG. 6 is a cross-sectional view schematically showing an operation of the control valve shown in FIGS. 2 and 3 in a second control mode.

FIG. 7 is a cross-sectional view schematically showing the operation of the control valve shown in FIGS. 2 and 3 in a third control mode.

FIG. 8 is a cross-sectional view schematically showing an operation of the control valve shown in FIGS. 2 and 3 in a fourth control mode.

FIG. 9 is a cross-sectional view schematically showing the operation of the control valve shown in FIGS. 2 and 3 in a fifth control mode.

FIG. 10 is a partially enlarged view of a portion A in FIG. 1;

FIG. 11 is a sectional view taken along line BB of FIG. 10;

FIG. 12 is a cross-sectional view showing a modification of the communication groove.

FIG. 13 is a partially enlarged view showing another modified example of the communication groove.

FIG. 14 is a graph showing a relationship between a suction flow rate between each suction port and a pump chamber and a rotor rotation angle in the present invention and the related art.

FIG. 15 is a view showing an opening shape of each suction port of a conventional oil pump device.

FIG. 16 is a view schematically showing a second embodiment of the oil pump device according to the present invention.

FIG. 17 is a detailed sectional view of the control valve shown in FIG.

18 is an enlarged view of a main part of the oil pump shown in FIG.

19 is a sectional view taken along line BB of FIG.

20 is a characteristic diagram showing a relationship between a rotation speed and a discharge amount obtained by the oil pump device shown in FIG.

FIG. 21 is a sectional view schematically showing an operation of the control valve shown in FIGS. 15 and 17 in a first control mode.

FIG. 22 is a sectional view schematically showing the operation of the control valve shown in FIGS. 15 and 17 in the second control mode.

FIG. 23 is a cross-sectional view schematically showing the operation of the control valve shown in FIGS. 15 and 17 in a third control mode.

FIG. 24 is a sectional view schematically showing the operation of the control valve shown in FIGS. 16 and 17 in a fourth control mode.

FIG. 25 is an enlarged view of a main part of an oil pump showing a modification of the opening shape.

FIG. 26 is a sectional view showing a modification of the communication groove.

FIG. 27 is a partial cross-sectional view showing a modification of the communication groove.

FIG. 28 is a graph showing the relationship between the discharge flow velocity between each discharge port and the pump chamber and the rotor rotation angle in the present invention and the prior art.

FIG. 29 is a view showing an opening shape of each discharge port of a conventional oil pump device.

[Explanation of symbols]

10, 310 Engine crankshaft (drive source) 20, 320 Oil pump 21, 321 Pump housing 21a Suction port 21b Discharge port 21c Main suction port (third in the first embodiment)
Port) 21d Sub suction port (second port in the first embodiment) 21e Discharge port (first port in the first embodiment) 21g, 21h, 121i, 321g, 321h, 32
1i Communication groove (suppression means) 30, 330 Control valve 50, 350 Feeding part 321a Suction port (first port in second embodiment) 321b Main discharge port (second port in second embodiment) 321c Sub discharge port (The third in the second embodiment
Port) 330a Inner hole 331a Main inflow port 331b Sub inflow port 331c Merging port 331d First return port 331e Second return port 341 Oil supply path 341a Main discharge path 341b Sub discharge path

Claims (3)

[Claims] An inner rotor having a plurality of external teeth, rotatably assembled in a pump housing and rotationally driven by a drive source having a variable number of rotations, meshing with the external teeth of the inner rotor, An outer rotor having a plurality of inner teeth defining a plurality of pump chambers between the outer teeth and rotatably assembled in the pump housing; and an outer rotor formed in the pump housing and different in a circumferential direction of the rotor. The first, second, and
A third port, and one pump chamber located between the first port and the second port has a maximum volume, and one of the second port and the third port in the rotation direction of the inner rotor. The first opening shape to the pump chamber at the end or the second opening shape to the pump chamber at the opposite rotation direction end of the inner rotor of the other of the second port and the third port, Pump means, which is defined so as to follow the interdental shape of the rotor constituting the pump chamber located between the second port and the third port, and controls the communication between the second port and the third port. An oil pump device configured to supply a predetermined amount of hydraulic oil to a portion to be supplied by pressure, wherein the rotation direction side end of one of the second port and the third port; Poe And the third
A change in the flow rate of the hydraulic oil between the second port and the third port with respect to a change in the volume of the pump chamber that defines the opening shape at at least one of the other ports and the opposite end in the anti-rotational direction. An oil pump device characterized by comprising means for suppressing pressure. 2. The control device according to claim 1, wherein the restricting unit is configured to control the rotation-side end of one of the second port and the third port or the anti-rotation direction of the other of the second port and the third port. The side end is connected to the second port and the third port.
The second port extends toward the rotation-direction end of the second port or the third port, and the second port extends through the pump chamber. The oil pump device according to claim 1, wherein a port and the third port are formed so as to communicate with each other. 3. The rotation control device according to claim 2, wherein the restraining unit includes one of the second port and the third port in the rotation direction, or the one of the second port and the third port in the non-rotational direction. The other end of the second port and the third port on the opposite side in the anti-rotational direction or the second port.
2. The oil pump device according to claim 1, comprising a communication groove formed to extend toward the rotation-side end of the other of the port and the third port. 3.