JPH06212932A - Lubricating feeder for engine - Google Patents

Abstract

PURPOSE:To reduce the driving loss of an oil pump in a lube oil feeder of an engine. CONSTITUTION:While a crank system orifice 21 for varying the flow path resistance is inserted in a crank system feed path 6, a valve system orifice 22 for varying the flow path resistance is interposed in a valve system feed path 5, and the flow path resistance of the crank system orifice 21 is reduced along with the increase of the rotational frequency of an engine, while a controller 20 for increasing the flow path resistance of the valve system orifice 22 is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improved engine lubricating oil supply system.

[0002]

2. Description of the Related Art As a conventional engine lubricating oil supply device, there is one shown in FIG. 13, for example (NISS
AN Sunny NX Coupe B13 type new car manual B-3
1 tribute, Nissan Motor Co., Ltd., issued in January 1990, see).

To explain this, a crank system in which a constant capacity oil pump 1 is driven by an engine and a lubricating oil discharged from the oil pump 1 is introduced from a discharge passage 2 to a main bearing 4 of a crankshaft. A supply passage 6 and a valve operating system supply passage 5 for supplying lubricating oil to the lubricating portion 3 of the valve operating system are branched and formed, and a fixed orifice 13 is arranged in the valve operating system supply passage 5. Reference numeral 7 is a regulator for suppressing the discharge pressure of the oil pump 1 to a predetermined value or less, 8 is an oil filter, and 9 is an oil pan.

As a result, as shown in FIG. 14, the flow rate of the lubricating oil in the crank system supply passage 6 gradually increases when the engine is rotating at a high speed, and sufficient lubricating oil is supplied to the main bearing 4 of the crankshaft while the valve operating valve is operated. The flow rate of lubricating oil in the system supply passage 5 is suppressed by the fixed orifice 13, and the lubricating portion 3 of the valve operating system 3
The flow rate of the lubricating oil supplied to the valve is prevented from becoming excessive, and the flow rate of the lubricating oil that lubricates the lubrication portion 3 of the valve operating system is suppressed so as not to exceed the recovery capacity of the passage 10 for returning to the oil pan 9. .

[0005]

Crank system supply passage 6
And the required flow rate of lubricating oil in the valve operating system supply passage 5 are shown in FIG.
In the conventional device in which the fixed orifice 13 is provided in the valve operating system supply passage 5, the flow rate of the lubricating oil in the valve operating system supply passage 5 changes at low engine speed. In order to secure Qa, the discharge pressure of the oil pump 1 has to be increased more than necessary, which causes a problem that the oil pump 1 becomes large and the drive loss of the oil pump 1 increases.

The present invention focuses on the above-mentioned problems and aims to reduce the drive loss of the oil pump.

[0007]

SUMMARY OF THE INVENTION According to the present invention, a constant capacity oil pump is driven by an engine, and a crank system supply passage for supplying lubricating oil discharged from the oil pump to a main bearing of a crankshaft is provided. In a lubricating oil supply device for an engine having a valve operating system supply passage for supplying lubricating oil discharged from an oil pump to a lubricating portion of a valve operating system, a crank having a variable passage resistance in a crank system supplying passage In addition to the system orifice, the valve system supply passage is provided with a valve operating system variable valve passage orifice, which reduces the passage resistance of the crank system orifice as the engine speed increases. In addition, a control device for increasing the flow path resistance of the valve operating system orifice is provided.

The invention according to claim 2 is, as a control device,
A spool valve that changes in the axial direction to change the flow passage areas of the crank system orifice and the valve system orifice, an electromagnetic actuator that drives the spool valve in the axial direction, a means for detecting operating conditions, and an electromagnetic actuator The control means drives according to an operating condition.

The invention according to claim 3 is as a control device,
A spool valve that changes in the axial direction to change the flow passage areas of the crank system orifice and the valve system orifice, and a return spring that urges the spool valve to the initial position,
A hydraulic chamber for guiding the discharge pressure of the oil pump to drive the spool valve against the return spring.

The invention according to claim 4 is as a control device,
A spool valve that changes in the axial direction to change the flow passage areas of the crank system orifice and the valve system orifice, and a return spring that urges the spool valve to the initial position,
A hydraulic chamber for guiding the discharge pressure of the oil pump to drive the spool valve against the return spring, and a temperature sensitive material for adjusting the urging force of the return spring according to the temperature of the lubricating oil are provided.

[0011]

According to the present invention, when the engine speed is low, the crank system orifice increases its flow passage resistance and the valve operating orifice reduces its flow passage resistance, thereby suppressing the discharge pressure of the oil pump. It is possible to secure a sufficient flow rate of the lubricating oil supplied to the lubricating portion of the valve train.

At the time of high engine speed, the crank system orifice reduces its flow passage resistance and the valve operating orifice increases its flow passage resistance, so that the main bearing of the crankshaft is suppressed while suppressing the discharge pressure of the oil pump. Ensuring a sufficient flow rate of lubricating oil and preventing the lubricating oil flow rate from being excessively supplied to the lubrication part of the valve operating system through the valve operating system supply passage. Keep the flow rate so that the recovery capacity of the passage for returning the lubricated lubricating oil to the oil pan is not exceeded.

Therefore, as in the conventional device in which the fixed orifice is provided in the valve system supply passage, the flow rate of the lubricating oil supplied to the lubricating portion of the valve system through the valve system supply passage at the time of low engine speed is controlled. It is not necessary to increase the discharge pressure of the oil pump to secure it, and the drive loss of the oil pump can be reduced.

According to the second aspect of the invention, the flow rate of the lubricating oil introduced to the main bearing of the crankshaft and the lubricating portion of the valve train can be finely controlled according to the engine operating conditions.

According to the third aspect of the present invention, by utilizing the discharge pressure of the oil pump which rises in accordance with the engine speed, the flow rate of the lubricating oil introduced to the main bearing of the crankshaft and the lubricating portion of the valve train is determined by the engine. The structure can be simplified by controlling according to the rotation speed.

According to the fourth aspect of the invention, the discharge pressure of the oil pump is utilized to control the flow rate of the lubricating oil introduced to the main bearing of the crankshaft and the lubricating portion of the valve train in accordance with the engine speed. The discharge pressure of the oil pump is prevented from fluctuating according to the lubricating oil temperature via the temperature sensitive material.

[0017]

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

As shown in FIGS. 1 and 2, the constant capacity oil pump 1 is driven by the engine 15, and the lubricating oil discharged from the oil pump 1 is guided to the oil filter 8 through the discharge side passage 2 to generate the oil. Lubricate the crank system supply passage 6 that supplies lubricating oil from the outlet of the filter 8 to the main bearing 4 of the crankshaft 11, and the lubrication portion 3 of the valve system that includes intake / exhaust valves 14i and 14e and camshafts 12i and 12e. A valve train supply passage 5 for supplying oil is branched. A crank system orifice 21 for varying the flow passage resistance is provided in the crank system supply passage 6, and a valve operating system orifice 22 for varying the flow passage resistance is provided in the valve operating system supply passage 5, so that the engine speed is The flow path resistance of the crank system orifice 21 is reduced as it rises, and
A control device 20 for increasing the flow path resistance of the valve operating system orifice 22 is provided.

In the figure, 7 is a regulator for suppressing the discharge pressure of the oil pump 1 to a predetermined value or less, and 9 is an oil pan.

As shown in FIG. 3, the cylinder block 1
6, a hole 17 intersecting the crank system supply passage 6 and the valve operating system supply passage 5 is formed, and the spool valve 18 is formed in the hole 17.
Is slidably mounted in the axial direction.

A through hole 23 communicating with the discharge side passage 2 is formed below the spool valve 18 in the hole 17, and a through hole 24 communicating with the valve operating system supply passage 5 is formed above the spool valve 18 in the hole 17. The lubricating oil is formed into and out of the hole 17 through the through holes 23 and 24 as the spool valve 18 is displaced,
The displacement of the spool valve 18 is not hindered.

The spool valve 18 has a crank system orifice 21 provided in the middle of the crank system supply passage 6 and a valve operating system orifice 22 provided in the valve operating system supply passage 5. As shown in FIG. 4, the cross sections of the orifices 21 and 22 are both formed into a keyhole shape. In this case, the structure is simplified by forming the two orifices 21 and 22 in the common spool valve 18.

When the spool valve 18 is in the initial position when it is seated at the bottom of the hole 17 as shown in the figure, the flow passage cross-sectional area of the crank system supply passage 6 is minimized and the flow passage of the valve operating system supply passage 5 is minimized. Maximum cross-sectional area. With the upward displacement of the spool valve 18 from this initial position, the flow passage cross-sectional area of the crank system supply passage 6 gradually increases and the flow passage cross-sectional area of the valve train supply passage 5 gradually decreases.

As the control device 20, a rod 25 screwed into the spool valve 18 and a servo motor (electromagnetic actuator) 26 for rotationally driving the rod 25 are provided.

A guide member 2 is attached to the upper end of the hole 17 and is provided with a guide member 29 for slidably penetrating the rod 25.
A seal ring 30 is interposed between 9 and the rod 19,
The hole 17 is sealed.

A rotation speed sensor 28 is provided as a means for detecting the engine rotation speed, and a detection signal of the rotation speed sensor 28 is input to the servo motor 2 according to the engine rotation speed.
A control unit 27 including a microcomputer or the like is provided as a control unit for driving the drive unit 6. The control unit 27 holds the spool valve 18 at the initial position when the engine speed is low, and pulls up the spool valve 18 as the engine speed increases.
To control.

Next, the operation will be described.

When the engine speed is low, the flow resistance of the crank system orifice 21 is large and the flow path resistance of the valve operating system orifice 22 is small. Therefore, the discharge pressure of the oil pump 1 is suppressed and the lubrication portion 3 of the valve operating system is supplied. A sufficient amount of lubricating oil flow is secured.

When the engine speed is high, the crank system orifice 21 reduces its flow passage resistance, and the valve operating system orifice 22 increases its flow passage resistance, so that the crankshaft 1 is suppressed while suppressing the discharge pressure of the oil pump 1.
1 while ensuring a sufficient flow rate of the lubricating oil supplied to the main bearing 4 and preventing the lubricating oil flow rate supplied to the lubricating portion of the valve operating system through the valve operating system supply passage 5 from becoming excessive, The flow rate of the lubricating oil that has lubricated the lubrication portion 3 of the valve train is suppressed so as not to exceed the recovery capacity of the passage 10 for returning to the oil pan 9.

As shown in FIG. 5, the control unit 27 controls the position of the spool valve 18 via the servo motor 26, so that the flow resistance of the crank system orifice 21 increases as the engine speed increases. Becomes smaller and the flow path resistance of the valve operating system orifice 22 becomes larger.

As a result, the lubricating oil flow rates of the crank system supply passage 6 and the valve operating system supply passage 5 change according to the engine speed as shown in FIG. 6, and the lubricating oil required for the engine shown in FIG. A flow rate can be secured.

The discharge pressure of the oil pump 1 changes as shown by the solid line in FIG. 7, and is suppressed to be smaller than that when the orifices 21, 22 are fixed as shown by the broken line in FIG.
The drive loss of the oil pump 1 can be reduced, and the oil pump 1
Can be miniaturized.

In this embodiment, the control unit 2
6, the lubricating oil flow rate can be finely controlled according to the engine speed.

Next, in another embodiment shown in FIG. 9, a return spring 31 for urging the spool valve 18 to the initial position.
And a hydraulic chamber 32 for guiding the discharge pressure of the oil pump 1 to drive the spool valve 18 against the return spring 31. The parts corresponding to those in FIG. 3 are designated by the same reference numerals.

The hydraulic chamber 32 is defined between the hole 17 and the spool valve 18, and communicates with the discharge side passage 2 through the through hole 33.

The return spring 31 is used for the spool valve 1
It is interposed in a compressed state between a recess 34 opened at the upper end of 8 and a recess 36 formed in the plug body 35.

When the engine is running at a low speed, the spool valve 18 is held by the biasing force of the return spring 31 at the initial position seated on the bottom of the hole 17 as shown in the figure, and the flow passage cross-sectional area of the crank system supply passage 6 is minimized. At the same time, the flow passage cross-sectional area of the valve train supply passage 5 is maximized.

Next, the operation will be described.

As the engine speed increases, the discharge pressure of the oil pump 1 introduced into the hydraulic chamber 32 increases, so that the spool valve 18 is displaced upward from the initial position against the return spring 31. . As a result, the flow passage resistance of the crank system orifice 21 is reduced and the flow passage resistance of the valve operating system orifice 22 is increased as the engine speed increases.

In this embodiment, by making the spool valve 18 respond to the discharge pressure of the oil pump 1, the number of parts can be reduced and the structure can be simplified.

Next, in another embodiment shown in FIG. 10, the return spring 3 for urging the spool valve 18 to the initial position.
1 and the discharge pressure of the oil pump 1 to guide the spool valve 18
Hydraulic chamber 32 that drives the engine against the return spring 31
And a temperature sensitive material 41 that weakens the biasing force of the return spring as the lubricating oil temperature rises.
The parts corresponding to those in FIG. 9 are designated by the same reference numerals.

The temperature sensitive material 41 is interposed between the recess 34 of the spool valve 18 and the return spring 31 via a spacer 42, and its expansion and contraction increases or decreases the spring load of the return spring 31.

The temperature sensitive material 41 is formed of a shape memory alloy or bimetal, and its axial length becomes shorter as its temperature rises as shown in FIG. 11, so that the biasing force of the return spring 31 is reduced. It is supposed to weaken.

Next, the operation will be described.

When the temperature is not corrected by the temperature sensitive material 41, the discharge pressure of the oil pump 1 changes according to the lubricating oil temperature, as shown in FIG.

During operation with a low lubricating oil temperature, the temperature sensitive material 41 strengthens the urging force of the return spring 31 and the spool valve 1
By delaying the movement of No. 8, the discharge pressure of the oil pump 1 can be maintained at the same level as when the lubricating oil is at a high temperature.

[0047]

As described above, according to the present invention, the constant capacity oil pump is driven by the engine, and the crank system supply passage is provided for supplying the lubricating oil discharged from the oil pump to the main bearing of the crankshaft. In addition, in a lubricating oil supply device for an engine, in which a valve operating system supply passage for supplying lubricating oil discharged from an oil pump to a lubricating portion of a valve operating system is arranged, a flow passage resistance of the crank system supplying passage is made variable. In addition to installing the crank system orifice, the valve system supply passage is provided with a valve operating system variable valve passage orifice, which increases the flow resistance of the crank system orifice as the engine speed increases. Since it has a control device that reduces the flow path resistance of the valve system orifice while making it smaller, it can be used for the main bearing of the crankshaft and the lubrication part of the valve system over a wide rotational speed range. Respectively can supply proper lubrication oil flow rate, without increasing more than necessary the discharge pressure of the oil pump, with an oil pump miniaturization can be achieved,
The drive loss of the oil pump can be reduced, and the fuel consumption and output of the engine can be improved.

According to the second aspect of the present invention, the flow rate of the lubricating oil introduced to the main bearing of the crankshaft and the lubricating portion of the valve train can be finely controlled according to the engine operating conditions.

According to the third aspect of the present invention, by utilizing the discharge pressure of the oil pump which rises in accordance with the engine speed, the flow rate of the lubricating oil introduced to the main bearing of the crankshaft and the lubricating portion of the valve train is changed to the engine speed. By controlling according to the number,
The structure can be simplified and the production cost can be reduced.

According to a fourth aspect of the present invention, by providing a temperature sensitive material that adjusts the biasing force of the return spring according to the temperature of the lubricating oil, the discharge pressure of the oil pump is used to move the main bearing of the crankshaft and the dynamic bearing. While controlling the flow rate of the lubricating oil guided to the lubrication section of the valve system according to the engine speed, it is possible to prevent the discharge pressure of the oil pump from varying via the temperature sensitive material according to the lubricating oil temperature. .

[Brief description of drawings]

FIG. 1 is a hydraulic circuit diagram showing an embodiment of the present invention.

FIG. 2 is a perspective view showing a hydraulic circuit of the engine.

FIG. 3 is a sectional view of the engine.

FIG. 4 is a sectional view taken along line AA of FIG.

FIG. 5 is a characteristic diagram of flow resistance of an orifice.

FIG. 6 is a characteristic diagram of a lubricating oil flow rate.

FIG. 7 is a characteristic diagram of pump discharge pressure.

FIG. 8 is a characteristic diagram of a lubricating oil flow rate required for the engine.

FIG. 9 is a cross-sectional view of an engine showing another embodiment.

FIG. 10 is a sectional view of an engine showing still another embodiment.

FIG. 11 is a characteristic diagram of the length of the temperature sensitive material.

FIG. 12 is a characteristic diagram of pump discharge pressure when a temperature sensitive material is not provided.

FIG. 13 is a hydraulic circuit diagram showing a conventional example.

FIG. 14 is a characteristic diagram of a lubricating oil flow rate.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Oil pump 2 Discharge side passage 3 Lubrication part of valve system 4 Main bearing of crankshaft 5 Valve system supply passage 6 Crank system supply passage 18 Spool valve 20 Controller 21 Crank system orifice 22 Valve system orifice 26 Servo motor ( Electromagnetic actuator) 27 Control unit 28 Rotation speed sensor 31 Return spring 32 Hydraulic chamber 41 Temperature sensitive material

Claims (4)

[Claims] Claim: What is claimed is: 1. A constant capacity oil pump is driven by an engine, and a crank system supply passage is provided for supplying lubricating oil discharged from the oil pump to a main bearing of a crankshaft. In a lubricating oil supply device for an engine in which a valve operating system supply passage for supplying oil to a lubricating portion of a valve operating system is arranged, a crank system orifice for varying the flow passage resistance is provided in the crank system supply passage, and A valve system orifice for varying the channel resistance is provided in the valve system supply passage to reduce the channel resistance of the crank system orifice as the engine speed increases, and A lubricating oil supply device for an engine, comprising a control device for increasing flow path resistance. 2. A control device, a spool valve that changes in the axial direction to change the flow passage areas of the crank system orifice and the valve operating system orifice, an electromagnetic actuator that drives the spool valve in the axial direction, and operating conditions. The lubricating oil supply device for an engine according to claim 1, further comprising: a means for detecting the above-mentioned condition, and a control means for driving the electromagnetic actuator according to operating conditions. 3. A control device, a spool valve that changes in the axial direction to change the flow passage areas of the crank system orifice and the valve operating system orifice, a return spring that biases the spool valve to an initial position, and an oil. The lubricating oil supply device for an engine according to claim 1, further comprising: a hydraulic chamber that guides a discharge pressure of the pump to drive the spool valve against the return spring. 4. A control device, a spool valve that changes in the axial direction to change the flow passage area of the crank system orifice and the valve operating system orifice, a return spring that urges the spool valve to an initial position, and an oil. A hydraulic chamber for guiding the discharge pressure of the pump to drive the spool valve against the return spring, and a temperature sensitive material for adjusting the biasing force of the return spring according to the temperature of the lubricating oil. 1. The engine lubricating oil supply device according to 1.