JP2543058Y2 - Oil pump pressure controller - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure control device for an oil pump, and more particularly to a pressure control device for a lubricating oil pump for an automobile engine or the like for appropriately controlling the discharge pressure according to the engine speed range. The present invention relates to a pressure control device.

[0002]

2. Description of the Related Art As a conventional control device provided for controlling the pressure of such an oil pump, for example,
Japanese Patent Application Laid-Open No. 3-19088 discloses one disclosed in FIG. This device is provided with a regulator valve for releasing oil from a discharge side of a pump, and is configured to relieve oil on a discharge side to a suction side through a plurality of relief ports by a valve body that operates according to a discharge pressure. .

[0003]

However, the conventional oil pump pressure control device is generally configured to be opened according to a predetermined discharge pressure, so that a high-speed rotation of an engine requiring high oil pressure is required. If the valve opening timing is adjusted so as to be suitable for the range, the hydraulic pressure is kept higher than necessary in the low-speed or middle-speed range, which causes an increase in horsepower consumption. Furthermore, although the above-described conventional example has a plurality of relief ports, the level of the hydraulic pressure changes slowly,
There was a problem that it was not possible to properly cope with the operating range of the engine.

An object of the present invention is to focus on the conventional problems as described above, and to solve the problems, an oil pump capable of appropriately and quickly adjusting the oil pressure of lubricating oil according to the engine speed range. Another object of the present invention is to provide a pressure control device.

[0005]

In order to achieve the above object, the present invention has a valve element which moves in a cylinder in accordance with oil pressure, and a plurality of relief passages provided in the cylinder. In a pressure control device of an oil pump capable of controlling an amount of oil relieved by displacement of a relative position of the valve body with respect to the relief passage at high pressure and low pressure of a hydraulic pressure guided to a cylinder, In the step of increasing the pressure to the high pressure, the amount of the oil to be relieved is narrowed down, and in the step of decreasing the pressure from the high pressure to the low pressure, the raising and lowering pressure is increased by increasing the amount of the relief oil. And a pressure increasing / decreasing assisting means which operates according to the displacement position of the valve element is provided at a position of the valve element relating to the relief passage.

[0006]

According to the present invention, in the process of raising and lowering the hydraulic pressure from the oil pump, the raising and lowering pressure assisting means operates according to the displacement position of the valve body, thereby narrowing the relief oil amount at the time of pressure raising, and at the time of pressure lowering. By increasing the relief oil amount, the hydraulic pressure switching speed can be increased, and an appropriate hydraulic pressure according to the high, medium, and low speed of the engine can be supplied.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the drawings.

FIG. 1 shows an embodiment of the present invention before the valve is opened. Here, 1 is a pressure control device (hereinafter referred to as a pressure control valve) according to the present invention for controlling the oil pressure of oil discharged from an oil pump (not shown), 2 is a discharge-side oil passage of the oil pump, 3 and Reference numeral 4 denotes first and second relief passages provided in the pressure control valve 1, respectively. Here, the second relief passage 4 has a larger diameter than the first relief passage 3. The pressure control valve 1 is provided with an outer cylinder 5 in which the relief passages 3 and 4 are formed, and an inner cylinder 6 having one end connected and fixed to the discharge cylinder 2 side of the outer cylinder 5. Thus, a piston-like valve element 7 is slidably fitted between the outer cylinder 5 and the inner cylinder 6.

Reference numeral 8 denotes a valve support spring interposed between the bottom 5A of the outer cylinder 5 and the valve body 7, and 9 denotes a back pressure release hole provided in the bottom 5A. Therefore, in a state where the oil pressure in the oil passage 2 does not exist or is kept sufficiently low, as shown in FIG.
Is kept deflected toward the lower end of the stopper 10 formed at the end of the inner cylinder 6. Reference numeral 6B denotes an oil hole formed in the inner cylinder fixed end 6A. The oil in the oil passage 2 is supplied to the cylinder chamber 11 between the outer cylinder 5 and the inner cylinder 6 through the oil hole 6B (see FIG. 2). See below). Furthermore, an inner cylinder passage 12 is formed along the center of the inner cylinder 6, and a communication between the inner cylinder passage 12 and the cylinder chamber 11 is provided by a third relief hole 13.

Reference numeral 6C denotes a cylindrical sliding groove provided along the outer peripheral lower half of the inner cylinder 6, and 14 is slidably fitted in the sliding groove 6C. The present invention that functions to increase the pressure raising / lowering speed at the time of hydraulic pressure level switching
Is a ring member as a step-up / down assisting means . Although the ring member 14 slides up and down along the sliding groove 6C of the inner cylinder 6 without any particular resistance, the ring member 14 is fitted to the inner peripheral surface 7D of the valve body 7 by a degree of fitting or use of a magnet. Due to this, it has a somewhat higher sliding resistance than the sliding groove 6C side. Therefore, when the valve element 7 moves up and down the cylinder chamber 11 as described later,
The ring member 14 operates integrally with the valve 7 as long as the ring member 14 contacts one of the upper and lower ends of the sliding groove 6C and its operation is not restricted. If the ring member 14 comes into contact with one of the upper and lower ends of the slide groove 6C during such an operation, the valve body 7 does not follow the movement of the valve body 7 in the same direction thereafter, and the peripheral surface 7
D and the outer peripheral surface of the ring member 14 are kept in sliding contact with each other.
In FIG. 11, the ring member 14 is in contact with the upper end of the sliding groove 6C, and in this state, the lower end of the ring member 14 is located on the upper edge of the second relief passage 4 and the third relief hole 1.
3 at the position corresponding to the upper edge.

On the other hand, a cylindrical passage (hereinafter, referred to as a valve body first passage) 7A provided along the outer peripheral surface of the inner cylinder 6 toward the valve body 7; A first valve hole 7B having a hole diameter substantially corresponding to the first relief passage, and formed substantially in a peripheral form closer to the second relief passage 4 than the passage 7B. Valve body second passage 7
C is provided.

Next, the operation of controlling the hydraulic pressure by the pressure control device of the oil pump constructed as described above will be described with reference to the following figures. FIGS. 2 to 5 show the behavior of the valve element 7 which operates according to the change in the hydraulic pressure as shown by A to G in FIG.

As shown in FIG. 1, when the hydraulic pressure is sufficiently low (indicated by A in FIG. 6), that is, in the lowest speed region of the engine, all of the relief passages 3 and 4 are connected to the valve body 7. It is closed by When the hydraulic pressure is gradually increased with the increase in the rotational speed and the state shown in FIG. 6B is reached, the valve body 7
The first relief passage 3 communicates with the oil passage 2 as shown in FIG. Thus, in the low-medium-speed rotation region (indicated by B to C to D in FIG. 6) accompanying the increase of the engine speed, the oil pressure can be unnecessarily increased by only the oil relief by the above-described thin first relief passage 3. Absent.

Next, at a point D in FIG. 6, which shifts to a high-speed rotation region where high oil pressure is required, the valve body 7 further descends in the cylinder chamber 11 by the oil pressure in that state, and the first relief passage 3 is closed. I do. In this case, the ring member 14 that behaves together with the valve body 7 abuts on the lower end of the sliding groove 6C while the valve body 7 operates from the state shown in FIGS. 2 Relief passage 4 is cut off. FIG. 3 shows such a relief passage in a closed state, which corresponds to a stage indicated by E in FIG.

Then, when the state becomes a high-speed rotation region and reaches a state of F in FIG. 6 in which a higher oil pressure is required, the first relief passage 3 is moved by the lowering position of the valve element 7 as shown in FIG. 6 and the second relief passage 4 simultaneously communicate with the oil passage 2, and in the subsequent rotation increase, the valve 7 shifts as shown in FIGS. As shown in G, the pressure is maintained at a stable high level.

As described above, when the engine shifts from low to medium speed to high speed, the oil to be relieved is temporarily interrupted via the ring member to quickly switch from low oil pressure to high oil pressure. Not only can it be possible, but also appropriate hydraulic pressure required at low, medium and high speeds can be maintained.

Next, a description will be given of the behavior of the valve element 7 when the hydraulic pressure is switched from the low hydraulic pressure to the high hydraulic pressure in the transition from the high speed range to the low / medium speed range with reference to FIGS.

When the hydraulic pressure rises as the engine speed increases in the high-speed range of the engine, that is, when FG and HI in FIG. 5 is maintained. Then, when the oil pressure drops to the state shown by I in FIG. 6, the valve element 7 returns to the position shown in FIG. 7, so that the oil in the oil passage 2 is further dashed in addition to the path indicated by the solid arrow. As shown by the arrow, the liquid is also guided from the third relief hole 13 to the second relief passage 4 through the gap at the lower end of the ring member 14. In the subsequent hydraulic pressure drop (state J in FIG. 6), the valve body 7 returns further upward, and escapes from the third relief hole 13 to the second relief passage 4 via the valve body second passage 7C. The oil rapidly increases, and the relief of the oil to the first relief passage 3 is stopped as shown in FIG. 8, but the return amount of the oil is increased by the second relief passage 4 having a larger diameter than the first relief passage 3. I do.

During operation from the state shown in FIG. 5 to the state shown in FIGS. 7 and 8, the ring member 14 is fitted in the sliding groove 6C of the inner cylinder 6 and is not restrained at the upper and lower ends. Accordingly, as described above, the ring member 14 moves together with the valve element 7 due to the biasing property of the valve element 7 due to magnetic force or the like. Thus, the ring member 14 is pulled upward in the sliding groove 6C together with the upward movement of the valve body 7,
In the state of FIG. 8, the space between the inner cylinder passage 12 and the second relief passage 4 can be kept completely open.
As shown by K, the hydraulic pressure can be rapidly reduced.

FIG. 9 shows a state in which the valve element 7 returns upward from the state of FIG. 8 due to a further decrease in oil pressure, closes the second relief passage 4, and connects the first relief passage 3 to the valve element first passage 7A, the first valve. The state where it was made to communicate via hole 7B is shown. Therefore, in this state, the amount of oil that has escaped has already been sufficiently reduced,
In the state indicated by L in FIG. 6, the descending gradient of the hydraulic pressure also becomes gentle. In addition, in the state of FIG.
Since the upper end of the valve member 4 comes into contact with the upper end of the slide groove 6C, the position of the ring member 14 is maintained as shown in FIG.

When the valve body 7 further rises from the state shown in FIG. 9 to the state shown as M in FIG. 6, the oil relief path shown by the arrow in FIG. 9 is further closed, and the return of the oil is stopped. Then, the original state shown in FIG. 1 (shown as N in FIG. 6) is obtained.

As described above, in order for the valve element to perform the operations shown in FIGS. 1 to 5 and FIGS. 7 to 9 in accordance with the hydraulic characteristics shown in FIG. Needless to say, the spring constant of the valve support spring 8 for moving the valve element is involved. That is, the relative positions of the components such as the oil passages provided in the valve body and the relief passages provided in the outer cylinder should also be set in relation to the selection of the spring. Although a single coil spring is used for the valve support spring 8 in the above-described embodiment, a combination of coil springs having different spring constants may be used.

[0023]

As described above, according to the present invention, in the process of increasing the hydraulic pressure from low pressure to high pressure, the amount of oil to be relieved is reduced, and the hydraulic pressure is reduced from high pressure to low pressure. In the pressure-lowering process, the pressure-releasing and boosting means that operates according to the displacement position of the valve element is related to the relief passage of the valve element so that the oil-relief amount increases and the pressure-elevating rate increases. Position, it is possible to quickly and appropriately switch the oil pressure between the high-speed rotation range of the engine where high oil pressure is required and the medium- and low-speed normal operation area where low oil pressure is sufficient, By supplying high oil pressure to the oil supply device, unnecessary horsepower can be consumed, and inconveniences such as the inability to obtain high oil pressure at high speed can be eliminated.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an example of the configuration of the present invention in a low hydraulic pressure state.

FIG. 2 is a diagram illustrating the operation of the pressure control device according to the present invention at the time of boosting.

FIG. 3 is an explanatory diagram of the operation of the pressure control device according to the present invention at the time of boosting.

FIG. 4 is an explanatory diagram of the operation of the pressure control device according to the present invention at the time of boosting.

FIG. 5 is an explanatory diagram of the operation of the pressure control device according to the present invention at the time of boosting.

FIG. 6 is a characteristic curve diagram showing the relationship between the hydraulic pressure and the engine speed obtained by the control operation of the present invention.

FIG. 7 is an explanatory diagram of the operation of the pressure control device according to the present invention at the time of pressure reduction.

FIG. 8 is an explanatory diagram of the operation of the pressure control device according to the present invention at the time of pressure reduction.

FIG. 9 is an explanatory diagram of the operation of the pressure control device according to the present invention at the time of pressure reduction.

[Description of Signs] 1 Pressure control device (pressure control valve) 2 Oil passage 3 First relief passage 4 Second relief passage 5 Outer cylinder 6 Inner cylinder 6B Oil hole 6C Sliding groove 7 Valve body 7A Valve body first passage 7B First valve hole 7C Valve body second passage 7D Peripheral surface of valve body 8 Valve support spring 11 Cylinder chamber 12 Inner cylinder passage 13 Third relief hole 14 Ring member

Claims (1)

(57) [Scope of request for utility model registration] 1. A valve body that moves in a cylinder in accordance with oil pressure, and a plurality of relief passages provided in the cylinder, wherein the valve body is provided when a hydraulic pressure guided to the cylinder is high and low. In the oil pump pressure control device capable of controlling the amount of oil relieved by the displacement of the relative position with respect to the relief passage, the amount of oil to be relieved is reduced in the process of increasing the oil pressure from a low pressure to a high pressure. A step-up / step-down assisting means that operates in accordance with the displacement position of the valve element so that the step-up / step-down speed is increased by increasing the amount of the relieved oil in the step of stepping down the pressure from the high pressure to the low pressure. The pressure control device of the oil pump, wherein the pressure valve is provided at a position related to the relief passage of the valve body.