JPH05187213A - Hydraulic control device for internal combustion engine - Google Patents

Abstract

PURPOSE:To feed enough lubricating oil meeting a demand by forming a plurality of relief passages opened by means of different pressures in response to an oil pressure and locating a variable orifice in the relief passage opened by means of a low pressure. CONSTITUTION:A valve body 13 is contained in the valve hole 12 of a control valve 11 opened to an oil pressure passage 10 connected to a main gallery, the valve body being energized through the force of a spring 14. A first relief port 16 is opened in the vicinity of a valve opening 15 and a second relief port 17 having a large bore is opened in a position spaced far away from the valve opening 15. Relief passages 18 and 19 connected to the relief ports 16 and 17 are opened to the return side and a variable orifice 20 is arranged to the relief port 18. The valve body 13 is moved backward according to the oil pressure of the oil pressure passage 10 and the relief ports 16 and 17 are opened according to a pressure. This constitution ensures an oil pressure meeting a demand and feeds adequate supply of high pressure lubricating oil according to a demand.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for controlling a lubricating oil pressure of an internal combustion engine.

[0002]

2. Description of the Related Art In a lubricating system of an internal combustion engine, the capacity of a lubricating oil pump is set in accordance with the high rotation speed of an engine requiring a large amount of oil, and a relief valve is provided so that the oil pressure does not rise above a certain level. However, in this case, when the load of the engine is small and the required oil amount is not so large, the pressure is increased by the amount beyond that, resulting in a drive loss of the pump.

Therefore, it has been proposed that the relief valve is provided with two relief ports and the loss of the pump is reduced by gradually opening these relief ports in response to the pressure of oil.

This is because when the required oil amount is not large,
By opening the first relief port at a predetermined low pressure and relieving the increased amount, the increase in pressure is suppressed, and at high rotation speed, the oil amount increases beyond the relief amount,
It keeps a predetermined pressure and delivers the required amount of oil.

The second relief port is a normal port that opens when the pressure reaches a certain upper limit (see Japanese Utility Model Laid-Open No. 60-72909).

[0006]

However, with such a structure, the required oil pressure cannot always be obtained at the time of high rotation and the like.

That is, the operation of the relief valve depends only on the set spring pressure of the valve, and since the first relief port has a constant port area, the oil amount increases as the rotation increases. However, the pressure rises only slowly and it is difficult to reach the required value.

Therefore, there is a concern that sufficient lubrication cannot be performed at high rotation speeds.

The object of the present invention is to solve such a problem.

[0010]

SUMMARY OF THE INVENTION According to the present invention, in a device for controlling hydraulic pressure from a lubricating oil pump of an internal combustion engine, a plurality of relief passages that open at different pressures in response to the hydraulic pressure are formed and at a low pressure. A variable orifice is provided in the open relief passage.

Further, in the device for controlling the hydraulic pressure from the lubricating oil pump of the internal combustion engine, the back pressure of the valve or the spring load of the valve that opens the relief passage in response to the hydraulic pressure is made variable.

[0012]

In other words, when the relief passage on the low pressure side is opened, the oil pressure is kept at a constant low pressure, but when the opening area of the variable orifice is reduced, the relief resistance increases and the pressure sharply rises. The smaller the area, the higher the pressure.

If any of the engine speed, engine load, pump speed, oil amount, oil temperature, and bearing ambient temperature exceeds the set value, sufficient lubrication is required. By reducing the opening area of, the required amount of oil can be sent at high pressure.

When the back pressure of the valve that opens the relief passage or the spring load of the valve is changed, that is, when the operating pressure of the valve is changed, the oil pressure changes.

Therefore, when any of the engine speed, the engine load, the pump speed, the oil amount, the oil temperature, and the bearing ambient temperature exceeds the set value, the back pressure of the valve or the spring load of the valve is increased. As a result, the pressure of the oil can be increased and the required amount of oil can be sent.

[0016]

Embodiments of the present invention will be described below with reference to the drawings.

1 to 4 are provided with a variable orifice in the relief passage, of which the variable orifice in FIG. 1 is the oil amount (flow rate) in the variable orifice, and in FIGS. 2 and 3 is the engine. Alternatively, the pump shown in FIG. 4 is operated by an electric actuator by rotating the pump.

First, in the case of FIG. 1, the valve body is freely slidable in a valve hole 12 of a control valve 11 opened in a hydraulic passage 10 connected to a main gallery from a lubricating oil pump (driven by an engine) (not shown). 13, a predetermined spring 14 for urging the valve body 13 toward the valve opening 15 is provided.

A valve opening 15 is provided on the side surface of the valve hole 12.
The first relief port 16 is opened at a predetermined position near the valve, and the second relief port 17 having a large diameter is opened at a predetermined position distant from the valve opening 15.

Relief passages 18 and 19 connected to the first and second relief ports 16 and 17 are opened to the return side (pump suction side) of an oil pan or the like after merging on the downstream side.

In response to the pressure of the oil in the hydraulic passage 10, the valve body 13 retracts from the valve opening 15 and the first pressure is maintained at a predetermined low pressure.
The relief port 16 is opened, and when the fixed upper limit value is reached, the second relief port 17 is further opened.

A variable orifice 20 is provided in the relief passage 18 connected to the first relief port 16.

The variable orifice 20 is provided in the relief passage 18
An orifice hole 22 is formed on the outlet side of an oil chamber 21 provided on the way of the valve body 2 for changing the opening area of the orifice hole 22.
3 penetrates through the partition wall 24 of the oil chamber 21 and is integrally provided at one end of a lever 25 which is swingably supported.

The lever 25 has a tip portion 26 extending to the center of the hydraulic passage 10 so as to also serve as a drag type flow rate detecting member, and urges the lever 25 toward the oil chamber 21 in the opening direction of the orifice hole 22. The spring 27 is inserted.

The lever 25 starts tilting in response to the flow of oil in the hydraulic passage 10, that is, when the amount of oil exceeds a predetermined value, and the opening area of the orifice hole 22 is reduced in accordance with this tilting.

That is, when the engine rotation is low and the amount of oil discharged from the lubricating oil pump is small, the valve body 13 of the control valve 11 is on the valve opening 15 side and the lever 25 of the variable orifice 20 is on the orifice hole 22. In the fully open position, in this case, a predetermined amount of oil is secured by sending the entire amount of oil from the pump from the main gallery to each part of the engine with hydraulic pressure according to the rotation of the pump.

When the amount of oil from the pump increases as the engine speed increases, and the hydraulic pressure increases, the valve body 13 of the control valve 11 begins to retract, and when it reaches a predetermined value, the first relief The port 16 is opened, and a part of the oil is relieved from the relief passage 18, whereby the hydraulic pressure is maintained at a predetermined low pressure.

In this case, the required amount of oil is not so large, the relief amount from the relief passage 18 increases as the amount of oil increases, and the hydraulic pressure is kept at a predetermined low pressure up to a predetermined engine speed range.

When the engine speed increases and the amount of oil from the pump further increases, the lever 25 begins to tilt due to the flow in the hydraulic passage 10, and the relief passage 1
The opening area of the orifice hole 20 of No. 8 decreases.

Then, the resistance of the relief passage 18 increases and the hydraulic pressure rises sharply.

As a result, the hydraulic pressure rises quickly when the engine is rotating at high speed, and a high hydraulic pressure can be secured.

At this time, the valve body 13 of the control valve 11 retracts by a predetermined amount in response to the hydraulic pressure, and when the engine speed further increases and the hydraulic pressure reaches the upper limit value, the valve body 13 further retracts. The second relief port 17 opens so that the hydraulic pressure does not exceed the upper limit.

As described above, when the engine rotation is not so high and the required amount of oil is not large, the relief passage 18 is opened to maintain the hydraulic pressure at a predetermined low pressure, thereby preventing the drive loss of the pump and the engine. When the rotation speed is high, the passage area of the relief passage 18 is reduced according to the oil amount, so that the hydraulic pressure can be quickly raised and the required amount of oil can be sent at a predetermined high pressure, and sufficient lubrication can be achieved at high rotation speeds. Can be secured.

The hydraulic pressure value in the main gallery is shown in FIG. 5, where the engine speed is N _{1 to} N ₂ (1500 to 4000r).
(set to pm) and becomes constant when the engine speed reaches N _{2 to} N ₃ (set to 4000 to 5000 rpm).

The alternate long and short dash line in FIG. 5 is the characteristic when the relief port 16 is not provided and shows the drive loss.

2 and 3, the gear 3 formed on the drive shaft 30 (connected to the engine) of the lubricating oil pump.
The rotary body 32 that meshes with 1 is provided with a variable orifice 34 that reduces the opening area of the orifice hole 33 by the centrifugal force during rotation, and the variable orifice 34 is provided in a relief passage 37 connected to the first relief port 36 of the control valve 35. There is.

The control valve 35 is similar to that shown in FIG. 1, and in response to the hydraulic pressure in the hydraulic passage 38, the valve body 40 in the valve hole 39 opens the first relief port 36 at a predetermined low pressure to maintain a constant upper limit value. Then, the second relief port 41 is opened.

The variable orifice 34 is a pair of valve bodies 42a, 42 which are slidably overlapped with each other in the radial direction of the rotating body 32.
b and a spring 43 for urging the valve elements 42a, 42b in the central direction, and when the rotational speed exceeds a predetermined value, the valve element 4
Orifice hole 3 between 2a and 42b sliding outward
The opening area of 3 is reduced.

The relief passage 37 is opened downstream of the orifice hole 33 in the gear chamber 44 around the rotary body 32, and after joining from the gear chamber 44 to the relief passage 45 connected to the second relief port 41, an oil pan or the like is formed. Open to the return side.

According to this, when the rotation of the lubricating oil pump, that is, the rotation of the engine is not high, the relief passage 37 can be opened to maintain the hydraulic pressure at a predetermined low pressure, while when the rotation of the engine is high, the pump can be maintained. With the rotation, the variable orifice 34 is directly driven to reduce the passage area of the relief passage 37, and high hydraulic pressure can be secured.

The hydraulic characteristics are the same as in FIG.

In FIG. 4, a valve body 52 for changing the opening area is provided on the outlet side of the first relief port 51 of the control valve 50, and a variable orifice 54 for driving the valve body 52 by an electric actuator 53 is formed. is doing.

The first relief port 51 is opened at a predetermined low hydraulic pressure, the second relief port 55 is opened when the hydraulic pressure reaches a certain upper limit value, and both ports 51 and 55 join in the oil chamber 56 on the outlet side. After that, it is open to the return side.

The electric actuator 53 has a control circuit 57.
Is controlled based on signals from a rotation sensor and a temperature sensor (not shown) that detect the rotation speed of the engine and the ambient temperature of the bearing that performs lubrication, and when the engine rotation is below the set value and around the bearing. When the temperature is below the set value, the valve body 52 is retracted and the relief port 5
Fully open the exit side of 1. On the other hand, when the rotation of the engine exceeds the set value or the temperature around the bearing exceeds the set value, the valve body 52 is advanced to close the outlet side of the relief port 51.

By doing so, the structure is simplified, and when the temperature of the bearing portion is high, the hydraulic pressure can be increased and a sufficient amount of lubricating oil can be sent.

The hydraulic pressure characteristic shown in FIG. 5 is obtained with respect to the engine rotation, but this can be set freely.

FIG. 6 shows a valve body 61 of the control valve 60.
Is directly driven by the electric actuator 62.

One slit-shaped relief port 64 connected to the return side is provided in the valve hole 63 of the control valve 60, and the control circuit 65 of the electric actuator 62 is provided with a rotation speed signal of the engine from a rotation sensor and a temperature sensor. A pressure sensor (not shown) that detects the bearing ambient temperature signal and the hydraulic pressure in the hydraulic passage 66 sends a hydraulic signal.

The electric actuator 62 includes a control circuit 65.
Accordingly, as shown in FIG. 7, when the engine speed Ne is equal to or lower than the set speed N ₁ (step 102 → 105), the hydraulic pressure Pm in the hydraulic passage 66 is set to the reference set pressure between the set speeds N _{1 and} N _2. When P ₁ is exceeded, the opening side is opened (steps 102, 10
3, 106 → 107), and at this time, when the pressure becomes equal to or lower than the reference set pressure P ₁ , it is driven to the close side (steps 106 → 108).

The engine speed Ne increases and the set engine speed N
_When it exceeds ₂ , it is closed (steps 103, 104 → 10
9) Further, when the set rotational speed N ₃ is exceeded and the hydraulic pressure Pm of the hydraulic passage 66 reaches the upper limit set pressure P ₂ , the opening side is opened (step 11
0 → 111) is driven.

On the other hand, the temperature Tm around the bearing portion is set to the set temperature T ₁
When it exceeds, it is driven to the closing side (step 101 → 105).

That is, the hydraulic pressure characteristic of FIG. 5 is obtained with respect to the engine rotation. Also in this case, of course, the amount of oil and the oil pressure can be freely set.

The embodiment of FIGS. 8 to 16 is such that the back pressure of the control valve or the spring load of the control valve is variable, and in FIG. 14 is changed by the rotation of the engine or pump, FIG. 14 is changed by an electric actuator, and FIG. 16 is changed by a spring load by an electric actuator.

In FIG. 8, the relief port 75 is provided at a predetermined position from the valve opening 74 on the side surface of the valve hole 73 accommodating the valve body 71 of the control valve 70 and the spring 72 for urging the valve body 71. The relief passage 76 connected to the relief port 75 is opened to the return side such as an oil pan.

An oil chamber 78, which also communicates with the hydraulic passage 77, is arranged in parallel in the valve hole 73, and orifice holes 79 and 80 are formed on the hydraulic passage 77 side of the oil chamber 78 and the outlet side connected to the relief passage 76, respectively. , Valve elements 81, 8 for changing the opening areas of these orifice holes 79, 80
2 is integrally provided on a lever 83 that also penetrates the oil chamber 78 and serves as a drag type flow rate detecting member.

The lever 83 is swingably supported via a pin at a substantially central position in the oil chamber 78, and the orifice hole 7
A predetermined spring 84 for urging the lever 83 in the direction of closing the valve body 81 of No. 9 in the direction of opening the valve body 82 of the orifice hole 80 is arranged.

The oil chamber 78 communicates with a back pressure chamber 86 on the side of the spring 72 of the valve body 71 of the valve hole 73 through a predetermined oil hole 85.

When the amount of oil flowing through the hydraulic passage 77 is not large, the orifice hole 79 of the oil chamber 78 is closed as shown in FIG.
The orifice 80 opens as shown in FIG.

When the amount of oil exceeds a predetermined amount, the lever 83 tilts, the orifice 79 opens, and the opening area of the orifice hole 80 decreases.

That is, when the engine speed is not high and the amount of oil from the lubricating oil pump is less than the predetermined value, the back pressure of the control valve 70 is almost 0, and therefore the valve body 71 is resisted against the spring 72. By opening the relief port 75, the hydraulic passage 7
The hydraulic pressure of 7 is maintained at a predetermined low pressure.

On the other hand, when the engine speed increases and the amount of oil exceeds a predetermined value, the orifice hole 79 opens according to the tilting of the lever 83, and the opening area of the orifice hole 80 decreases, so that the pressure in the oil chamber 78 decreases. Control valve 70
Back pressure increases.

As a result, the operating pressure of the control valve 70, that is, the relief pressure is increased, so that a high hydraulic pressure can be secured.

When the pressure on the hydraulic passage 77 side is Pm, the pressure in the oil chamber 78 is Pb, and the flow path resistances of the orifice holes 79 and 80 are k ₁ and k ₂ , the flow rate Qr through the orifice holes 79 and 80 is Since they are the same, Pm = (k ₁ + k ₂ ) Qr ² (1) Pb = k ₂ Qr ² (2) From equations (1) and (2), Pb = Pm (k ₂ / k ₁ + k ₂ (3) The relief pressure Pr of the control valve 70 is Pr = KΔx + Pb (4) Pr = Pm (5), where K is the spring constant of the spring 72 and Δx is the amount of displacement of the valve body 71. From equations (3) to (5), Pr = KΔx (1 + k ₁ / k ₂ ) ... (6) Therefore, the relief pressure becomes (1 + k ₁ / k ₂ ) times.

When the pressure on the hydraulic passage 77 side reaches the relief pressure, the relief port opens and the upper limit value is not exceeded.

This hydraulic characteristic is shown in FIG.

The control valve 90 shown in FIGS.
A small orifice hole 94 for guiding the hydraulic pressure of the hydraulic passage 92 to the back pressure chamber 93 is formed in the valve body 91 of the rotary body 97, and a rotary body 97 that meshes with a gear 96 formed on a drive shaft 95 of the lubricating oil pump.
A variable orifice 98 similar to that shown in FIGS.
The return passage 99 of the back pressure chamber 93 (relief passage 100
Connected to)).

Each part of the variable orifice 98 is shown in FIGS.
The same reference numeral is given.

According to this, when the rotation of the lubricating oil pump, that is, the engine is high, the variable orifice 98 can be directly driven to increase the back pressure of the control valve 90, and the relief pressure can be increased.

In the structure shown in FIG. 14, the lever shown in FIG. 8 is connected to the electric actuator 101 for driving. In this case, the tip of the lever 102 has the hydraulic passage
Does not protrude to 3.

Control circuit 10 of electric actuator 101
Reference numeral 4 denotes a set rotation speed when the rotation of the engine is equal to or lower than the set rotation speed as shown in FIG. 15 based on the engine rotation speed signal and the load signal from the rotation sensor and the load sensor (not shown). When it exceeds the limit, the actuator 101 is moved forward (steps 204 to 20).
6) When the load is low, the set speed is increased, and when the load is high, the set speed is decreased (step 2).
01-203).

That is, similarly to when the engine speed is high, when the load is high, it is possible to increase the hydraulic pressure and sufficiently feed the lubricating oil.

The other parts are given the same reference numerals as in FIG.

FIG. 16 shows an electric actuator 111 for changing the spring load of the control valve 110.

A rack bar 115 is disposed via a retainer 114 at the rear end of a spring 113 that biases the valve body 112 of the control valve 110 to the closing side, and the rack bar 115 is slid by a step motor 116.

Signals are sent to the control circuit 117 from a rotation sensor, a pressure sensor that detects the discharge pressure of the lubricating oil pump 118, and an oil temperature sensor (not shown) that detects the lubricating oil temperature. The motor 116 is drive-controlled.

By doing so, of course, when the engine speed is high, or when the oil temperature is high and the pressure is hard to rise, the hydraulic pressure can be increased and a sufficient amount of lubricating oil can be sent.

119 is an oil pan, 120, 12
Reference numeral 1 denotes a cylinder head and a cylinder block.

[0078]

As described above, according to the present invention, in a device for controlling a hydraulic pressure from a lubricating oil pump of an internal combustion engine, a plurality of relief passages that open at different pressures in response to the hydraulic pressure are formed and at a low pressure. Since the variable orifice is provided in the open relief passage, it is possible to secure the hydraulic pressure that meets the demand, and to prevent the drive loss of the pump and to supply the lubricating oil sufficiently at the predetermined high pressure when the required amount of the lubricating oil is large. ..

Also, by varying the back pressure of the valve or the spring load of the valve that opens the relief passage in response to the hydraulic pressure, it is possible to secure the hydraulic pressure that also meets the demand, and to prevent the drive loss of the pump and the lubricating oil. It is possible to sufficiently feed the lubricating oil at a predetermined high pressure when the required amount is large.

[Brief description of drawings]

FIG. 1 is a sectional view of a first embodiment.

FIG. 2 is a sectional view of a second embodiment.

FIG. 3 is a sectional view of the variable orifice portion.

FIG. 4 is a sectional view showing the configuration of a third embodiment.

FIG. 5 is a hydraulic characteristic diagram.

FIG. 6 is a sectional view of the structure of a fourth embodiment.

FIG. 7 is a control flowchart thereof.

FIG. 8 is a sectional view of a fifth embodiment.

FIG. 9 is a cross-sectional view showing an opened state of an orifice hole.

FIG. 10 is a cross-sectional view showing an opened state of an orifice hole.

FIG. 11 is a hydraulic characteristic diagram.

FIG. 12 is a sectional view of a sixth embodiment.

FIG. 13 is a sectional view of the variable orifice portion.

FIG. 14 is a sectional view showing the configuration of a seventh embodiment.

FIG. 15 is a control flowchart thereof.

FIG. 16 is a sectional view showing the structure of an eighth embodiment.

[Explanation of symbols]

 10 Hydraulic Passage 11 Control Valve 13 Valve Body 14 Spring 16 First Relief Port 17 Second Relief Port 18 Relief Passage 19 Relief Passage 20 Variable Orifice 22 Orifice Hole 23 Valve Body 25 Lever 27 Spring 32 Rotating Body 33 Orifice Hole 34 Variable Orifice 35 Control valve 36 First relief port 37 Relief passage 38 Hydraulic passage 40 Valve body 41 Second relief port 42a, 42b Valve body 43 Spring 45 Relief passage 50 Control valve 51 First relief port 52 Valve body 53 Electric actuator 54 Variable Orifice 55 Second Relief Port 57 Control Circuit 60 Control Valve 61 Valve Disc 62 Electric Actuator 64 Relief Port 65 Control Circuit 66 Hydraulic Passage 70 Control Valve 71 Valve Disc 72 Spring 75 Relief port 76 Relief passage 77 Hydraulic passage 78 Oil chamber 79 Orifice hole 80 Orifice hole 81 Valve body 82 Valve body 83 Lever 84 Spring 86 Back pressure chamber 90 Control valve 91 Valve body 92 Hydraulic passage 93 Back pressure chamber 94 Orifice hole 97 Rotating body 98 variable orifice 100 relief passage 101 electric actuator 102 lever 103 hydraulic passage 104 control circuit 110 control valve 111 electric actuator 112 valve disc 113 spring 115 rack bar 116 step motor 117 control circuit

Claims (2)

[Claims] 1. A device for controlling a hydraulic pressure from a lubricating oil pump of an internal combustion engine, wherein a plurality of relief passages that open at different pressures in response to the hydraulic pressure are formed, and a variable orifice is provided in the relief passage that opens at a low pressure. A hydraulic control device for an internal combustion engine, characterized in that 2. A device for controlling a hydraulic pressure from a lubricating oil pump of an internal combustion engine, wherein a back pressure of a valve for opening a relief passage in response to the hydraulic pressure or a spring load of the valve is variable. Hydraulic control device.