JP2010150988A - Lubricating oil supply device of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating oil supply device of an internal combustion engine capable of appropriately determining its abnormality, as to a hydraulic control mechanism for switching pressure of a lubricating oil supplied to a lubricating portion of the internal combustion engine. <P>SOLUTION: In the lubricating oil supply device 40 of the engine 10, the pressure of a supply passage 42 for supplying the lubricating oil to the lubricating portion of the engine 10 by an engine driven oil pump 43 is controlled by the hydraulic control mechanism 50. The lubricating oil supply device 40 includes the hydraulic control mechanism 50 that releases the lubricating oil to a predetermined portion when a supply pressure P supplied from the supply passage 42 to the control mechanism 50 exceeds a predetermined relief pressure. Whether the hydraulic control mechanism 50 has any abnormality or not is determined based on change of engine operation state when an instruction is transmitted to the hydraulic control mechanism 50 to switch a predetermined relief pressure. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a lubricating oil supply device for an internal combustion engine that controls a pressure of a supply passage for supplying lubricating oil to a lubricating portion of the internal combustion engine by an engine-driven oil pump by a hydraulic control mechanism.

As the lubricating oil supply device, for example, the one described in Patent Document 1 is known.
In conventional lubricating oil supply devices including those described in this document, the relief pressure of the hydraulic control valve is switched between the low-pressure relief pressure and the high-pressure relief pressure to supply the lubrication part of the internal combustion engine. The pressure of the lubricating oil is controlled.
JP-A-6-101439

  By the way, for example, if an abnormality occurs in the hydraulic control valve in a state where the relief pressure on the low pressure side is set, even if a command for switching the relief pressure to the relief pressure on the high pressure side is transmitted from the control device, the relief actually The pressure is never switched. At this time, since the pressure of the lubricating oil in the supply passage is still maintained at a level corresponding to the relief pressure on the low pressure side, the engine seizure occurs due to insufficient lubrication at the lubrication part of the internal combustion engine. It is also possible to imitate. Similarly, if an abnormality occurs in the hydraulic control valve in the state where the relief pressure on the high pressure side is set, excessive lubrication oil is supplied to the lubrication part of the internal combustion engine, resulting in deterioration of fuel consumption. To come to.

  In any case, in order to cope with problems caused by abnormalities in hydraulic control mechanisms including the hydraulic control valve, it is first required to properly determine abnormalities in the control mechanism. No technical proposals have been made. Note that this can be said to be generally common to any specific configuration of the lubricating oil supply device that controls the pressure of the lubricating oil by switching the relief pressure of the hydraulic control mechanism.

  The present invention has been made in view of such a situation, and an object of the present invention is to appropriately determine the abnormality of the hydraulic control mechanism that switches the pressure of the supply passage that supplies the lubricating oil to the lubrication part of the internal combustion engine. An object of the present invention is to provide a lubricating oil supply device for an internal combustion engine.

In the following, means for achieving the above object and its effects are described.
(1) The invention according to claim 1 controls the pressure of the supply passage for supplying the lubricating oil to the lubrication part of the internal combustion engine by the engine-driven oil pump by the hydraulic control mechanism. In the lubricating oil supply apparatus for an internal combustion engine, the hydraulic control is provided with a device that relieves the lubricating oil to a predetermined portion when the pressure of the lubricating oil supplied from the supply passage to the control mechanism exceeds a predetermined relief pressure. And a determination unit that determines whether or not an abnormality has occurred in the hydraulic control mechanism based on a change in an engine operation state when a command to switch the predetermined relief pressure is transmitted to the mechanism. It is said.

  When the hydraulic control mechanism operates to switch the predetermined relief pressure from the low-pressure side relief pressure to the high-pressure side relief pressure, the driving force required in the oil pump increases accordingly. Appears as a change in driving conditions. That is, when a command to switch the predetermined relief pressure is transmitted to the hydraulic control mechanism, but no corresponding change is observed in the engine operating state, the hydraulic control mechanism responds to the command. Will not work.

  In view of the above, in the present invention, since the determination unit determines whether or not an abnormality has occurred in the hydraulic control mechanism, it can be appropriately determined that an abnormality has occurred in the control mechanism. It becomes like this.

  (2) According to a second aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the first aspect, the determination means increases the predetermined relief pressure by a predetermined amount with respect to the hydraulic control mechanism. The gist is to determine that an abnormality has occurred in the hydraulic control mechanism based on the fact that no change in engine load corresponding to the direction of change in the relief pressure has occurred when a command to decrease is transmitted. Yes.

  (3) According to a third aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the first or second aspect, the determination means supplies the predetermined relief pressure to the low pressure side with respect to the hydraulic control mechanism. When a command to switch from the first relief pressure to the second relief pressure on the high pressure side is transmitted, it is determined that an abnormality has occurred in the hydraulic control mechanism based on the fact that no increase in engine load has occurred. This is the gist.

  When the hydraulic control mechanism operates to switch the predetermined relief pressure from the first relief pressure to the second relief pressure, the driving force required in the oil pump increases accordingly, and this increase in driving force Appears as a change in load. That is, when an increase in engine load is not observed despite a command for switching from the first relief pressure to the second relief pressure being transmitted, the hydraulic control mechanism operates in accordance with the command. Will not be.

  In view of the above, in the present invention, since the determination unit determines whether or not an abnormality has occurred in the hydraulic control mechanism, it can be appropriately determined that an abnormality has occurred in the control mechanism. It becomes like this.

  (4) According to a fourth aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to any one of the first to third aspects, the determination means is configured to apply the predetermined relief to the hydraulic control mechanism. When the command to switch the pressure from the second relief pressure on the high pressure side to the first relief pressure on the low pressure side is transmitted, an abnormality occurs in the hydraulic control mechanism based on the fact that the engine load is not reduced. The gist is to determine that it is.

  When the hydraulic control mechanism operates to switch the predetermined relief pressure from the second relief pressure to the first relief pressure, the driving force required in the oil pump is reduced accordingly, and this reduction in the driving force is caused by the engine. Appears as a change in load. In other words, when the engine load is not reduced even though a command for switching from the second relief pressure to the first relief pressure is transmitted, the hydraulic control mechanism operates in accordance with the command. Will not be.

  In view of the above, in the present invention, since the determination unit determines whether or not an abnormality has occurred in the hydraulic control mechanism, it can be appropriately determined that an abnormality has occurred in the control mechanism. It becomes like this.

  (5) The invention according to claim 5 is the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 4, wherein the hydraulic control mechanism is configured to supply the lubricating oil discharged from the oil pump. The hydraulic control valve is configured to relieve the lubricating oil to the upstream side of the oil pump based on the pressure exceeding the predetermined relief pressure. The hydraulic control valve reduces the predetermined relief pressure to the first low pressure side. Between the relief pressure and the second relief pressure on the high pressure side, and the hydraulic control valve is configured to change the predetermined relief pressure when the operation state is maintained in the first operation state. The relief pressure is set to 1 and the predetermined relief pressure is set to the second relief pressure when the operation state is maintained in the second operation state.

  In the present invention, when the hydraulic control valve is set to the first relief pressure by the switching valve, the hydraulic pressure discharged from the oil pump rises and becomes equal to or higher than the first relief pressure. The valve opens and the lubricating oil is relieved. As a result, the hydraulic pressure supplied to each part of the engine is maintained at a pressure corresponding to the first relief pressure. Further, when the hydraulic control valve is set to the second relief pressure by the switching valve, when the hydraulic pressure discharged from the oil pump increases and becomes equal to or higher than the second relief pressure, the hydraulic control valve is opened and excessive. New lubricant is released. Thereby, the hydraulic pressure supplied to each part of the engine becomes the second relief pressure.

  (6) According to a sixth aspect of the present invention, in the lubricating oil supply apparatus for an internal combustion engine according to the fifth aspect, the determination means applies the predetermined relief pressure to the first relief pressure with respect to the hydraulic control mechanism. Based on the fact that no increase in engine load has occurred when a command to switch from pressure to the second relief pressure is transmitted, the hydraulic control valve is in the first operating state as an abnormality of the hydraulic control mechanism. The gist is to determine that it is fixed.

  When the hydraulic control valve is stuck in the first operating state, the control valve is maintained in the first operating state regardless of the command to switch the relief pressure from the control device. There will be no changes resulting from the directive. In view of the above, in the present invention, the sticking of the hydraulic control valve is determined according to the mode by the determination means, so that it is possible to more appropriately determine that an abnormality has occurred in the hydraulic control mechanism. Become.

  (7) The invention according to claim 7 is the lubricating oil supply device for an internal combustion engine according to claim 5 or 6, wherein the determination means applies the predetermined relief pressure to the hydraulic control mechanism by the second pressure. When the command to switch from the relief pressure to the first relief pressure is transmitted, no decrease in engine load occurs, so that the hydraulic control valve is The gist is to determine that it is fixed in the operating state.

  When the hydraulic control valve is stuck in the second operating state, the control valve is maintained in the second operating state regardless of the command to switch the relief pressure from the control device. There will be no changes resulting from the directive. In view of the above, in the present invention, the sticking of the hydraulic control valve is determined according to the mode by the determination means, so that it is possible to more appropriately determine that an abnormality has occurred in the hydraulic control mechanism. Become.

  (8) According to an eighth aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to any one of the fifth to seventh aspects, the hydraulic control mechanism is located upstream of the oil pump in the supply passage. And a control passage connecting the downstream side and the downstream side of the oil pump based on the fact that the pressure of the lubricating oil provided in the control passage and discharged from the oil pump exceeds the predetermined relief pressure The hydraulic control valve is configured to include a switching mechanism that operates the hydraulic control valve to switch the predetermined relief pressure, and the hydraulic control valve is an oil chamber that retains lubricating oil. A valve body that is formed in the oil chamber and moves relative to the valve body, and a movable body that is provided between the valve body and the valve body and moves relative to the valve body. Consists of including The valve body communicates the main body inlet communicating the control passage and the oil chamber on the downstream side of the oil pump, and the control passage and oil chamber on the upstream side of the oil pump. And the movable body is provided between the main body inlet and the oil chamber and communicates with the movable inlet, and the main body outlet and the oil chamber. A movable outlet that is provided between and communicates with each other, and moves between a first movable position and a second movable position with respect to the valve body, In addition, the main body inlet and the movable inlet are in communication with each other and the main body outlet and the movable outlet are in communication with each other when the first movable position and the second movable position are in the first movable position and the second movable position. The valve body is the valve body At least the first valve body range near the movable inlet and the second valve body range farther away from the movable inlet and further away from the movable inlet. Any one of a third valve body range and a fourth valve body range that is further away from the movable inlet can be taken, and the first valve body range can be set regardless of the position of the movable body. When the movable inlet and the movable outlet are interrupted to interrupt the flow of lubricating oil from the main body inlet to the main body outlet, and when the movable body is in the first movable position When in the second valve body range, the movable inlet and the movable outlet are communicated to allow the flow of lubricating oil from the main body inlet to the main body outlet, and the movable body is The second When the movable valve is in the third valve body range when in the movable position, the gap between the movable inlet and the movable outlet is blocked to block the flow of lubricating oil from the main body inlet to the main body outlet, When the movable body is in the second movable position and in the fourth valve body range, the movable inlet communicates with the movable outlet, and the hydraulic control valve is movable When the body is in the first movable position, the first operating state is set, and when the movable body is in the second movable position, the second operating state is set, and the switching mechanism is The gist of the invention is that the predetermined relief pressure is switched between the first relief pressure and the second relief pressure by manipulating the position of the movable body.

  (9) The invention according to claim 9 is the lubricating oil supply device for an internal combustion engine according to claim 8, wherein the switching mechanism is configured such that the oil is provided between the valve body and the movable body in the hydraulic control valve. A switching chamber provided separately from the chamber, a movable passage branched from the control passage and connected to the switching chamber, and supply of lubricating oil from the control passage to the switching chamber via the movable passage The movable body is set to the first movable position based on the supply of lubricating oil to the switching chamber via the movable passage. The hydraulic control valve is set to the second movable position based on the supply of lubricating oil to the switching chamber being cut off, and the hydraulic control valve is configured such that the movable body is moved to the first movable position. The predetermined relief pressure based on being maintained The predetermined relief pressure is set to the second relief pressure based on the fact that the movable body is maintained at the second movable position, and the determination means includes: An abnormality occurs in at least one of the valve body, the movable body, and the switching valve based on a change in engine operating state when a command to switch the predetermined relief pressure is transmitted to the hydraulic control mechanism. The gist is to determine whether or not.

1 to 8, an embodiment in which the lubricating oil supply device for an internal combustion engine according to the present invention is embodied as an electronically controlled lubricating oil supply device for a vehicle will be described.
As shown in FIG. 1, the engine 10 includes an engine main body 20 that generates power through combustion of a mixture of air and fuel, a lubricating oil supply device 40 that supplies lubricating oil to each lubricating portion of the engine 10, and these devices. And an electronic control unit 60 that controls the entire system.

  The engine body 20 is provided with a cylinder block 21 that burns a mixture of fuel supplied to the combustion chamber 30 via the injector 26 and air supplied to the combustion chamber 30 through the intake device. The cylinder block 21 is provided with a plurality of cylinders 22 each forming a combustion chamber 30. A piston 23 is provided in the cylinder 22. The piston 23 is connected to a connecting rod 24 that converts the reciprocating motion into a rotational motion and transmits it to the crankshaft 25.

  An oil pan 41 for storing lubricating oil is provided at the lower portion of the cylinder block 21. The lubricating oil in the oil pan 41 is supplied to each lubricating part of the engine body 20 through an oil pump 43 driven by the crankshaft 25.

  The lubricating oil supply device 40 supplies the lubricating oil in the oil pan 41 to each lubricating part of the engine body 20 through the supply passage 42. In the middle of the supply passage 42, there is provided an oil pump 43 that draws lubricating oil from the oil pan 41 and discharges it. An oil strainer 44 that filters relatively large foreign substances contained in the lubricating oil in the oil pan 41 is provided at the inlet of the supply passage 42. An oil filter 45 that filters minute foreign matters contained in the lubricating oil is provided in the vicinity of the downstream side of the oil pump 43 in the supply passage 42.

  In the lubricating oil supply device 40, the lubricating oil discharged from the oil pump 43 in the supply passage 42 is returned to the upstream side of the pump 43, whereby the pressure of the lubricating oil in the supply passage 42 (hereinafter referred to as “supply hydraulic pressure P”). ) Is provided.

  The hydraulic control mechanism 50 is provided with a relief passage 53 that connects the upstream side and the downstream side of the oil pump 43 in the supply passage 42. The relief passage 53 is opened when the pressure of the lubricating oil discharged from the oil pump 43 becomes equal to or higher than a predetermined relief pressure (hereinafter referred to as “relief pressure PX”). A relief valve 51 for returning the lubricating oil is provided from the side to the upstream side. The relief passage 53 is connected to a switching valve passage 54 for supplying lubricating oil on the inlet side of the relief valve 51 to the switching chamber 57 d of the valve 51. The switching valve passage 54 is provided with a switching valve 52 for switching the open / closed state of the passage 54.

  The switching valve 52 switches the relief pressure PX of the relief valve 51 by controlling the supply mode of the lubricating oil to the switching chamber 57d. That is, when lubricating oil is supplied to the switching chamber 57d when the switching valve 52 is in the open state, the relief pressure PX of the relief valve 51 is the first relief pressure on the low pressure side (hereinafter referred to as “first relief pressure P1”). )) And when the supply of the lubricating oil to the switching chamber 57d is shut off due to the switching valve 52 being closed, the relief pressure PX of the relief valve 51 is higher than the first relief pressure P1. The second relief pressure (hereinafter referred to as “second relief pressure P2”).

  When the relief pressure PX is set to the first relief pressure P1, the relief valve 51 opens based on the supply hydraulic pressure P exceeding the first relief pressure P1, and thereby the lubrication discharged from the oil pump 43 is performed. The oil is relieved upstream of the pump 43. Further, when the relief pressure PX is set to the second relief pressure P2, the valve is opened based on the supply hydraulic pressure P exceeding the second relief pressure P2, and the lubricating oil discharged from the oil pump 43 is supplied to the pump 43. Relief upstream.

  The lubricating oil supply device 40 includes an oil pan 41, a supply passage 42, an oil pump 43, an oil strainer 44, an oil filter 45, and a hydraulic control mechanism 50. The switching mechanism includes a switching chamber 57d, a switching valve passage 54, and a switching valve 52.

  The electronic control unit 60 grasps the engine operation state, the vehicle running state, and the driver's request based on signals from various sensors including an accelerator position sensor 61, a throttle position sensor 62, a crank position sensor 63, and an air flow meter 64. Then, for example, the following control is performed. That is, control such as throttle control for adjusting the intake flow rate, injection control for adjusting the fuel injection amount by the injector 26, and hydraulic control for controlling the hydraulic pressure supplied to each lubricating part of the engine is performed.

  The accelerator position sensor 61 outputs a signal corresponding to the depression amount of the accelerator pedal of the vehicle. The throttle position sensor 62 outputs a signal corresponding to the opening of the throttle valve. The crank position sensor 63 outputs a signal corresponding to the rotational speed of the crankshaft (hereinafter referred to as “engine rotational speed NE”). The air flow meter 64 outputs a signal corresponding to the mass flow rate of the intake air flowing through the intake passage.

  Here, in the hydraulic pressure control, the switching valve 52 is controlled so as to supply the hydraulic pressure suitable for the engine operating state grasped based on the signals of the various sensors to each lubricating part of the engine body 20. Specifically, the relief pressure PX is set to the first relief pressure P1 through the control of the switching valve 52 when the engine speed NE is in the low rotation range or the middle rotation range. On the other hand, when the engine rotation speed NE is in the high rotation region, the relief pressure PX is set to the second relief pressure P2 through the control of the switching valve 52.

A specific configuration of the hydraulic control mechanism 50 will be described in detail with reference to FIG. In the figure, a portion surrounded by a broken line indicates a relief valve 51.
The hydraulic control mechanism 50 includes a relief passage 53 that connects the upstream side and the downstream side of the oil pump 43 in the supply passage 42, and the pressure of the lubricating oil that is provided in the relief passage 53 and discharged from the oil pump 43 is a relief pressure. A relief valve 51 that relieves lubricating oil to the upstream side of the oil pump 43 based on exceeding PX, and a switching valve 52 that operates the relief valve 51 to switch the relief pressure PX are configured.

  The relief valve 51 is provided with a cylindrical housing 55. The housing 55 is formed with an oil chamber 56 for retaining lubricating oil. The oil chamber 56 is provided with a cylindrical sleeve 57. The sleeve 57 moves in the axial direction (hereinafter, “axial direction X”) with respect to the housing 55. The oil chamber 56 inside the sleeve 57 is provided with a columnar piston 58. The piston 58 moves in the axial direction X with respect to the housing 55 and the sleeve 57.

  The housing 55 has a housing inlet 55b that communicates the relief passage 53 downstream of the oil pump 43 and the oil chamber 56, and a housing outlet 55c that communicates the relief passage 53 upstream of the oil pump 43 and the oil chamber 56. And are formed. At both ends in the axial direction X of the housing 55, one of them is closed by the bottom wall 55a and the other is released.

  The sleeve 57 is located between the housing inlet 55b and the oil chamber 56 and communicates with the sleeve inlet 57b. The sleeve 57 is located between the housing outlet 55c and the oil chamber 56 and communicates with the sleeve outlet 57c. Is formed. At both ends in the axial direction X of the sleeve 57, one of them is closed by the bottom wall 57a and the other is released.

  The sleeve 57 is provided in the housing 55 in such a manner that the opening in the axial direction X opens in the same direction as the opening of the housing 55, and the outer peripheral surface of the sleeve 57 contacts the inner peripheral surface of the housing 55. . Thereby, when the sleeve 57 moves to the bottom wall 55a side to the maximum with respect to the housing 55, the bottom wall 57a of the sleeve 57 and the bottom wall 55a of the housing 55 contact each other.

  The openings of the housing 55 and the sleeve 57 are closed by a closing body 59 formed as a separate body. The closing body 59 is fixed to the housing 55 and the sleeve 57 in a state where the main body portion 59a is inserted into the opening of the sleeve 57 and the flange portion 59b is abutted against the end surface 55e of the housing 55. .

  The sleeve 57 has a position where the end surface 57e abuts against the flange portion 59b of the closing body 59 from a position where the bottom wall 57a abuts against the bottom wall 55a of the housing 55 (hereinafter, “first movable position X1”). X2 ") is allowed to move relative to the housing 55. Further, a force is applied from the first movable position X1 to the second movable position X2 by a separate spring. The housing inlet 55b and the sleeve inlet 57b are in communication with each other and the housing outlet 55c and the sleeve outlet 57c are in communication with each other at the first movable position X1 and the second movable position X2. .

  When the sleeve 57 is in the first movable position X1, a switching chamber 57d for retaining lubricating oil is formed between the end surface 57e of the sleeve 57 and the flange portion 59b of the closing body 59. In the housing 55, a switching port 55d for connecting the switching valve passage 54 and the switching chamber 57d is provided at a position corresponding to the switching chamber 57d.

  When the sleeve 57 is at the second movable position X2, the switching chamber 57d is not formed between the end surface 57e of the sleeve 57 and the flange portion 59b of the closing body 59 due to contact.

  The piston 58 is located at least in a range close to the sleeve inlet 57b as a position relative to the housing 55 (hereinafter referred to as “first opening / closing range Y1”), and in a range further away from the sleeve inlet 57b (hereinafter referred to as “ 2nd opening / closing range Y2 "), a range further away from the sleeve inlet 57b (hereinafter," third opening / closing range Y3 "), and a range further away from the sleeve inlet 57b (hereinafter referred to as" third opening / closing range Y3 "). , “Fourth open / close range Y4”).

  Here, the first opening / closing range Y1 is between the sleeve inlet 57b and the sleeve outlet 57c, that is, between the sleeve outlet 57c and the oil chamber 56 regardless of the position of the sleeve 57, and from the housing inlet 55b to the housing outlet 55c. The range of the position of the piston 58 that blocks the flow of the lubricating oil is shown.

  Further, the second opening / closing range Y2 communicates between the sleeve inlet 57b and the sleeve outlet 57c, that is, between the sleeve outlet 57c and the oil chamber 56 when the sleeve 57 is in the first movable position X1, and from the housing inlet 55b. The range of the position of the piston 58 which permits the flow of the lubricating oil to the housing outlet 55c is shown. Since the first opening / closing range Y1 and the second opening / closing range Y2 are continuous ranges, the position of the piston 58 farthest from the bottom wall 57a in the first opening / closing range Y1 and the bottom wall 57a in the second opening / closing range Y2 The position of the piston 58 closest to is substantially the same.

  Further, the third opening / closing range Y3 is configured such that when the sleeve 57 is in the second movable position X2, the space between the sleeve inlet 57b and the sleeve outlet 57c, that is, between the sleeve outlet 57c and the oil chamber 56, is blocked from the housing inlet 55b. The range of the position of the piston 58 which interrupts | blocks the flow of the lubricating oil to the housing exit 55c is shown. Since the second opening / closing range Y2 and the third opening / closing range Y3 are continuous ranges, the position of the piston 58 farthest from the bottom wall 57a in the second opening / closing range Y2 and the bottom wall 57a in the third opening / closing range Y3. The position of the piston 58 closest to is substantially the same.

  The fourth opening / closing range Y4 communicates between the sleeve inlet 57b and the sleeve outlet 57c, that is, between the sleeve outlet 57c and the oil chamber 56 when the sleeve 57 is in the second movable position X2, and from the housing inlet 55b. The range of the position of the piston 58 which permits the flow of the lubricating oil to the housing outlet 55c is shown. Since the third opening / closing range Y3 and the fourth opening / closing range Y4 are continuous ranges, the position of the piston 58 farthest from the bottom wall 57a in the third opening / closing range Y3 and the bottom wall 57a in the fourth opening / closing range Y4. The position of the piston 58 closest to is substantially the same.

The operation mode of the hydraulic control mechanism 50 will be described with reference to FIGS. 3 and 4.
FIG. 3 shows a change in the operation mode of the hydraulic control mechanism 50 as the supply hydraulic pressure P increases when the switching valve 52 is in the open state, that is, when the sleeve 57 is in the first movable position X1.

  As shown in FIG. 3A, when the supply hydraulic pressure P is less than the first relief pressure P1, the piston 58 is held near the bottom wall 57a of the sleeve 57 due to the relationship between the supply hydraulic pressure P and the spring 56d. Is done. That is, the position of the piston 58 with respect to the housing 55 is held within the first opening / closing range Y1.

  Thereby, the space between the sleeve inlet 57b and the sleeve outlet 57c is blocked through the piston 58, and the flow of the lubricating oil from the housing inlet 55b to the housing outlet 55c is also blocked. For this reason, the lubricating oil supplied to the relief valve 51 is not relieved, and the supply hydraulic pressure P tends to increase rapidly toward the first relief pressure P1. In addition, the piston 58 moves in a direction away from the bottom wall 57a due to the increase in the supply hydraulic pressure P, but is maintained in the first opening / closing range Y1 until the supply hydraulic pressure P reaches the first relief pressure P1. .

  As shown in FIG. 3B, when the supply hydraulic pressure P exceeds the first relief pressure P1, the piston 58 moves from the bottom wall 57a beyond the first opening / closing range Y1 due to the relationship between the supply hydraulic pressure P and the spring 56d. It is held at a distance. That is, the position of the piston 58 with respect to the housing 55 is held within the second opening / closing range Y2.

  As a result, the sleeve inlet 57b and the sleeve outlet 57c communicate with each other, and the lubricating oil flow from the housing inlet 55b to the housing outlet 55c is allowed. For this reason, the lubricating oil supplied to the relief valve 51 is relieved upstream of the oil pump 43. At this time, although the supply hydraulic pressure P tends to increase with an increase in the discharge amount of the oil pump 43, the degree thereof becomes gentler than when the supply hydraulic pressure P is less than the first relief pressure P1. Further, although the piston 58 moves further away from the bottom wall 57a due to the increase in the supply hydraulic pressure P, the supply hydraulic pressure P is the same as described above as long as the relief pressure PX is set to the first relief pressure P1. Shows a gradual upward trend.

FIG. 4 shows a change in the operation mode of the hydraulic control mechanism 50 as the supply hydraulic pressure P increases when the switching valve 52 is in the closed state, that is, when the sleeve 57 is in the second movable position X2.
As shown in FIG. 4 (A), when the supply hydraulic pressure P is between the first relief pressure P1 and the second relief pressure P2, the piston 58 is in the second state due to the relationship between the supply hydraulic pressure P and the spring 56d. It is held at a position farther from the bottom wall 57a than the opening / closing range Y2. That is, the position of the piston 58 with respect to the housing 55 is held within the third opening / closing range Y3.

  Here, the position of the piston 58 farthest from the bottom wall 57a in the second opening / closing range Y2 and the position of the piston 58 closest to the bottom wall 57a in the third opening / closing range Y3 are substantially the same position, When the sleeve 57 is in the second movable position X2, it is located farther from the housing inlet 55b than when it is in the first movable position X1. Therefore, immediately after the sleeve 57 is switched from the first movable position X1 to the second movable position X2, when the piston 58 is at the position farthest from the bottom wall 57a in the second opening / closing range Y2, the piston 58 moves to the position of the piston 58. Even when there is no substantial change, the sleeve inlet 57b is closed by the piston 58 unlike when the sleeve 57 is in the first movable position X1 (FIG. 3B). As long as the piston 58 is within the third opening / closing range Y3, this state is maintained.

  Thereby, the space between the sleeve inlet 57b and the sleeve outlet 57c is blocked through the piston 58, and the flow of the lubricating oil from the housing inlet 55b to the housing outlet 55c is also blocked. For this reason, the lubricating oil supplied to the relief valve 51 is not relieved, and the supply hydraulic pressure P tends to increase rapidly toward the second relief pressure P2. In addition, the piston 58 moves in a direction away from the bottom wall 57a due to the increase in the supply hydraulic pressure P, but is maintained in the third opening / closing range Y3 until the supply hydraulic pressure P reaches the second relief pressure P2. .

  As shown in FIG. 4B, when the supply hydraulic pressure P exceeds the second relief pressure P2, the piston 58 is separated from the bottom wall 57a more than the third opening / closing range Y3 due to the relationship between the supply hydraulic pressure P and the spring 56d. Held in place. That is, the position of the piston 58 with respect to the housing 55 is held in the fourth opening / closing range Y4.

  As a result, the sleeve inlet 57b and the sleeve outlet 57c communicate with each other, and the lubricating oil flow from the housing inlet 55b to the housing outlet 55c is allowed. For this reason, the lubricating oil supplied to the relief valve 51 is relieved upstream of the oil pump 43. At this time, although the supply hydraulic pressure P tends to increase as the discharge amount of the oil pump 43 increases, the degree thereof becomes gentler than when the supply hydraulic pressure P is less than the second relief pressure P2.

  When a request for switching the relief pressure PX to the first relief pressure P1 occurs when the sleeve 57 is in the second movable position X2, it is formed in the housing 55 separately from the oil chamber 56 and the switching chamber 57d. Lubricating oil is supplied to the auxiliary chamber. That is, the switching valve 52 is opened and the lubricating oil in the relief passage 53 is supplied to the auxiliary chamber via the switching valve passage 54. Accordingly, the sleeve 57 moves from the second movable position X2 toward the first movable position X1 through the hydraulic pressure in the auxiliary chamber.

With reference to FIG. 5, the relationship between the engine speed NE and the supply hydraulic pressure P will be described.
When the engine rotational speed NE is in a region smaller than the first rotational speed NE1, the sleeve 57 is held at the first movable position X1, and the supply hydraulic pressure P is less than the first relief pressure P1, whereby the piston 58 is It is held in the first opening / closing range Y1. That is, the relief valve 51 is in a state where the relief pressure PX is set to the first relief pressure P1 and is closed. As a result, the supply hydraulic pressure P tends to increase rapidly toward the first relief pressure P1 as the engine rotational speed NE increases.

  When the engine rotational speed NE exceeds the first rotational speed NE1, the supply hydraulic pressure P becomes larger than the first relief pressure P1, and the piston 58 is pushed down to the second opening / closing range Y2. Thereby, the relief valve 51 is opened and a part of the lubricating oil discharged from the oil pump 43 is relieved to the upstream side of the pump 43.

  When the engine rotational speed NE is in a region greater than the first rotational speed NE1 and smaller than the second rotational speed NE2, the sleeve 57 is held at the first movable position X1, and the supply hydraulic pressure P is the first relief pressure P1. As a result, the piston 58 is held in the second opening / closing range Y2. That is, the relief valve 51 is in a state where the relief pressure PX is set to the first relief pressure P1 and opened. As a result, the supply hydraulic pressure P increases as the engine rotational speed NE increases, but the degree of increase due to the relief valve 51 being opened is compared with the case where the engine rotational speed NE is smaller than the first rotational speed NE1. And become gradual.

  When the engine rotational speed NE exceeds the second rotational speed NE2, the sleeve 57 is switched from the first movable position X1 to the second movable position X2 based on this. That is, the relief pressure PX of the relief valve 51 is switched from the first relief pressure P1 to the second relief pressure P2. Thereby, since the sleeve outlet 57c is closed by the piston 58, the relief valve 51 is closed and the lubricating oil is not relieved.

  When the engine rotational speed NE is in a region larger than the second rotational speed NE2 and smaller than the third rotational speed NE3, the sleeve 57 is held at the second movable position X2 and the supply hydraulic pressure P is set to the second relief pressure P2. By being less than this, the piston 58 is held in the third opening / closing range Y3. That is, the relief valve 51 is in a state where the relief pressure PX is set to the second relief pressure P2 and is closed. As a result, the supply hydraulic pressure P tends to increase rapidly as the engine speed NE increases.

  When the engine rotational speed NE exceeds the third rotational speed NE3, the supply hydraulic pressure P becomes larger than the second relief pressure P2, and the piston 58 is pushed down to the fourth opening / closing range Y4. Thereby, the relief valve 51 is opened and a part of the lubricating oil discharged from the oil pump 43 is relieved to the upstream side of the pump 43.

  When the engine rotational speed NE is in a region greater than the third rotational speed NE3, the sleeve 57 is held at the second movable position X2, and the supply hydraulic pressure P is equal to or higher than the second relief pressure P2, whereby the piston 58 is It is held in the fourth opening / closing range Y4. That is, the relief valve 51 is in a state where the relief pressure PX is set to the second relief pressure P2 and is opened. As a result, the supply hydraulic pressure P increases as the engine rotational speed NE increases, but the degree of increase due to the relief valve 51 being opened increases the engine rotational speed NE to the second rotational speed NE2 and the third rotational speed NE3. Compared to the case between

  With reference to FIG. 6, the content of the “supply hydraulic pressure control process” executed as such hydraulic pressure control will be described. This process is repeatedly executed at predetermined control intervals by the electronic control unit 60 during operation of the engine 10.

  In this process, first, in step S110, it is determined whether or not the engine speed NE is in a high speed region. This determination can be made based on, for example, whether or not the engine speed NE grasped through the crank position sensor 63 is equal to or higher than a predetermined determination value.

  If it is determined in step S110 that the engine rotational speed NE is in the high rotation region, the relief pressure PX of the relief valve 51 is set to the second relief pressure P2 in the next step S120. That is, the energization to the switching valve 52 is cut off. On the other hand, when it is determined that the engine rotation speed NE is not in the high rotation region, the relief pressure PX of the relief valve 51 is set to the first relief pressure P1 in the next step S130. That is, energization to the switching valve 52 is executed.

  By the way, when an abnormality occurs in the hydraulic control mechanism 50 with the relief pressure PX set to the first relief pressure P1, a command for switching the relief pressure PX to the second relief pressure P2 is transmitted from the electronic control unit 60. Even if it is done, the relief pressure PX is not actually switched. At this time, since the pressure of the lubricating oil in the supply passage 42 is still maintained at a level corresponding to the first relief pressure P1, the engine 10 It is also conceivable to mimic the seizure. Similarly, when an abnormality occurs in the hydraulic control mechanism 50 with the relief pressure PX set to the second relief pressure P2, excessive lubricating oil is supplied to the lubrication part of the engine 10. As a result, fuel consumption will deteriorate.

  On the other hand, in the engine 10 provided with the engine-driven oil pump 43, the resistance on the discharge side of the oil pump 43 changes with the change of the relief pressure PX of the hydraulic control mechanism 50, so the engine operating state also changes accordingly. Will come to show.

  That is, when the relief pressure PX is switched from the first relief pressure P1 to the second relief pressure P2, the engine speed NE decreases due to the increase in resistance of the oil pump 43 accompanying this. At this time, the fuel injection amount and the intake air amount are increased to compensate for the decrease in the engine rotational speed NE through the control by the electronic control unit 60. Therefore, the decrease in the engine rotational speed NE is a temporary change. When the pressure PX is appropriately switched, the phenomenon itself that the engine rotational speed NE decreases is surely generated if it is normal.

  Further, when the relief pressure PX is switched from the second relief pressure P2 to the first relief pressure P1, the engine speed NE rises due to a decrease in resistance of the oil pump 43 accompanying this. At this time, since the fuel injection amount and the intake air amount are decreased to compensate for the increase in the engine speed NE through the control by the electronic control unit 60, the increase in the engine speed NE becomes a temporary change, but the relief When the pressure PX is appropriately switched, the phenomenon that the engine rotational speed NE rises will surely occur if it is normal.

  Thus, when the hydraulic control mechanism 50 performs the operation of switching the relief pressure PX, the driving force required in the oil pump 43 increases accordingly, and this increase in driving force is caused by the engine load (fuel injection amount or suction). Appears as a change in air volume. That is, when a command to switch the relief pressure PX is transmitted to the hydraulic control mechanism 50 but no corresponding change is observed in the engine load, the hydraulic control mechanism 50 responds to the command. Will not work.

  In view of this, in the present embodiment, whether or not an abnormality has occurred in the relief valve 51 based on a change in the engine load when a command to switch the relief pressure PX is transmitted to the hydraulic control mechanism 50. Is determined. That is, when an instruction to switch from the first relief pressure P1 to the second relief pressure P2 is transmitted, an increase in engine load is not confirmed, or a command to switch from the second relief pressure P2 to the first relief pressure P1. When a decrease in engine load is not confirmed when is transmitted, it is determined that an abnormality has occurred in the hydraulic control mechanism 50 based on this.

  With reference to FIG. 7, a detailed processing procedure of “low pressure side abnormality determination process” executed as a process for diagnosing abnormality of the hydraulic control mechanism 50 in the above manner will be described. Note that this processing is repeatedly executed at every predetermined calculation cycle while the engine 10 is in operation. Further, after the diagnosis that the abnormality of the hydraulic control mechanism 50 has occurred, the execution of the process is suspended until the operation of the engine 10 is stopped.

  In the abnormality determination process, first, in step S210, a command for switching the relief pressure PX of the relief valve 51 from the first relief pressure P1 to the second relief pressure P2 (hereinafter, “high pressure relief signal”) is given to the valve 51. To send. Note that the high-pressure relief signal is forcibly transmitted for this abnormality determination separately from the request for switching the relief pressure PX based on the engine speed NE.

  In the next step S220, it is determined whether or not an increase in engine load has occurred after the high-pressure relief signal has been transmitted. Specific examples of this determination include the following. That is, when the high-pressure relief signal is transmitted and the fuel injection amount of the injector 26 increases, it can be determined based on this that an increase in engine load has occurred. Alternatively, when the high-pressure relief signal is transmitted, it can be determined that an increase in the engine load has occurred based on the increase in the intake air amount. It should be noted that the determination related to the increase in engine load can be performed using other parameters that serve as an index of engine load, regardless of the method based on the fuel injection amount or the intake air amount exemplified here.

  When it is determined in step S220 that an increase in engine load has occurred, that is, it is estimated that the hydraulic control mechanism 50 has performed an operation of switching the relief pressure PX from the first relief pressure P1 to the second relief pressure P2 based on the high pressure relief signal. When this is done, a diagnosis is made that there is no abnormality in the valve 51. In step S230, the relief pressure PX is switched from the second relief pressure P2 to the first relief pressure P1 in order to return the relief pressure PX switched for the abnormality determination process to the original state.

  On the other hand, when it is determined in step S220 that the engine load has not increased, that is, the high pressure relief signal is transmitted to the hydraulic pressure control mechanism 50, the mechanism 50 reduces the relief pressure PX to the first relief pressure P1. When it is estimated that the operation of switching to the second relief pressure P2 is not performed, a diagnosis is made that an abnormality has occurred in the hydraulic control mechanism 50.

  By the way, the main abnormality considered to occur in this case is that the sleeve 57 of the relief valve 51 is fixed to the housing 55, the piston 58 is fixed to the sleeve 57, or the switching valve 52. Are fixed in a valve-open state. Therefore, when it is diagnosed through step S220 that an abnormality has occurred, this abnormality is not considered to have occurred in any part of the hydraulic control mechanism 50, but the abnormality occurrence part is identified as the sleeve 57, the piston 58, It can also be specified as at least one of the switching valves 52. The distinction between the abnormality occurrence portions can be made clear by, for example, the type of data stored in the memory in the next step S240.

  In the process of step S240, data indicating that an abnormality has occurred in the relief valve 51 is stored in the memory, and a warning lamp for notifying the driver is turned on, and then the engine 10 is evacuated, that is, the vehicle Perform evacuation travel. An example of the retreat travel is one that sets an upper limit of the engine rotational speed NE.

  After performing the process of step S240, the execution of the abnormality determination process is suspended until the operation of the engine 10 is stopped. When the abnormality of the relief valve 51 is resolved through the maintenance of the engine 10 and the data stored in the memory is erased, the abnormality determination process is executed again in the same manner as described above when the engine 10 is subsequently operated. Will come to be.

  With reference to FIG. 8, a detailed processing procedure of “high-pressure side abnormality determination processing” executed as processing for diagnosing abnormality of the hydraulic control mechanism 50 in the above-described manner will be described. Note that this processing is repeatedly executed at every predetermined calculation cycle while the engine 10 is in operation. Further, after the diagnosis that the abnormality of the hydraulic control mechanism 50 has occurred, the execution of the process is suspended until the operation of the engine 10 is stopped.

  In the abnormality determination process, first, in step S310, a command for switching the relief pressure PX of the relief valve 51 from the second relief pressure P2 to the first relief pressure P1 (hereinafter, “low pressure relief signal”) is sent to the valve 51. To send. Note that the low-pressure relief signal is forcibly transmitted for this abnormality determination separately from the request for switching the relief pressure PX based on the engine speed NE.

  In the next step S320, it is determined whether or not a reduction in engine load has occurred after the low pressure relief signal has been transmitted. Specific examples of this determination include the following. That is, when the low pressure relief signal is transmitted and the fuel injection amount of the injector 26 decreases, it can be determined that the engine load has decreased based on this. Alternatively, when the low-pressure relief signal is transmitted, it can be determined that the engine load has decreased based on the decrease in the intake air amount. It should be noted that the determination relating to the reduction of the engine load can be performed using other parameters serving as an index of the engine load regardless of the method based on the fuel injection amount or the intake air amount exemplified here.

  When it is determined in step S320 that the engine load has decreased, that is, it is estimated that the hydraulic control mechanism 50 has performed an operation of switching the relief pressure PX from the second relief pressure P2 to the first relief pressure P1 based on the low pressure relief signal. When this is done, a diagnosis is made that there is no abnormality in the valve 51. In step S330, the relief pressure PX is switched from the first relief pressure P1 to the second relief pressure P2 so as to return the relief pressure PX switched for the abnormality determination process to the original state.

  On the other hand, when it is determined in step S320 that the engine load has not decreased, that is, the low pressure relief signal is transmitted to the hydraulic control mechanism 50, the mechanism 50 reduces the relief pressure PX to the second relief pressure P2. When it is estimated that the operation of switching to the first relief pressure P1 is not performed, a diagnosis is made that an abnormality has occurred in the hydraulic control mechanism 50.

  By the way, the main abnormality considered to occur in this case is that the sleeve 57 of the relief valve 51 is fixed to the housing 55, the piston 58 is fixed to the sleeve 57, or the switching valve 52. Is fixed in a closed state. Therefore, when it is diagnosed through step S120 that an abnormality has occurred, this abnormality is not considered to have occurred in any part of the hydraulic control mechanism 50, but the abnormality occurrence part is identified as the sleeve 57, the piston 58, It can also be specified as at least one of the switching valves 52. For example, a method of clarifying the abnormality occurrence site by the type of data stored in the memory in the next step S340 can be used.

  In step S340, data indicating that the abnormality has occurred in the relief valve 51 is stored in the memory, and a warning lamp for notifying the driver is turned on. Perform evacuation travel. An example of the retreat travel is one that sets an upper limit of the engine rotational speed NE.

  After executing the process of step S340, the execution of the abnormality determination process is suspended until the operation of the engine 10 is stopped. When the abnormality of the relief valve 51 is resolved through the maintenance of the engine 10 and the data stored in the memory is erased, the abnormality determination process is executed again in the same manner as described above when the engine 10 is subsequently operated. Will come to be.

According to the lubricating oil supply device for an internal combustion engine of the present embodiment, the following effects can be obtained.
(1) In the present embodiment, whether or not an abnormality has occurred in the hydraulic control mechanism 50 based on a change in the engine operating state when a command to switch the relief pressure PX is transmitted to the hydraulic control mechanism 50. Judgment is made. This makes it possible to appropriately determine whether or not an abnormality has occurred in the hydraulic control mechanism 50.

  (2) In this embodiment, when a command to switch the relief pressure PX from the first relief pressure P1 on the low pressure side to the second relief pressure P2 on the high pressure side is transmitted to the hydraulic control mechanism 50, the engine load Based on the fact that no increase has occurred, it is determined that an abnormality has occurred in the hydraulic control mechanism 50. As a result, it is possible to appropriately determine that an abnormality has occurred in the hydraulic control mechanism 50.

  (3) In this embodiment, when a command to switch the relief pressure PX from the second relief pressure P2 on the high pressure side to the first relief pressure P1 on the low pressure side is transmitted to the hydraulic control mechanism 50, the engine load Based on the fact that no decrease has occurred, it is determined that an abnormality has occurred in the hydraulic control mechanism 50. As a result, it is possible to appropriately determine that an abnormality has occurred in the hydraulic control mechanism 50.

(4) In the present embodiment, it is determined whether an abnormality has occurred in the hydraulic control mechanism 50 based on the engine load. Thereby, abnormality diagnosis of the hydraulic control mechanism 50 can be performed without using a hydraulic sensor.
(Other embodiments)
The embodiment of the present invention is not limited to the above-described embodiment, and can be modified as shown below, for example.

  In the above embodiment, it is determined whether an abnormality has occurred in the mechanism 50 based on a change in the engine load when a command to switch the relief pressure PX is transmitted to the hydraulic control mechanism 50. However, the parameter indicating the engine operating state used for abnormality determination is not limited to the engine load. For example, whether or not an abnormality has occurred in the hydraulic control mechanism 50 can also be determined based on the amount of change in the engine speed NE when a command for switching the relief pressure PX is transmitted. That is, a decrease in the engine speed NE when the hydraulic pressure control mechanism 50 operates to switch the relief pressure PX from the first relief pressure P1 to the second relief pressure P2 is set in advance as a judgment value, and is switched to this judgment value. Compared with the actual change amount of the engine speed NE when a command to that effect is transmitted, if the change amount is smaller than the determination value, an abnormality has occurred in the hydraulic control mechanism 50 based on this change amount. It can also be determined. Further, an increase in the engine speed NE when the hydraulic pressure control mechanism 50 operates to switch the relief pressure PX from the second relief pressure P2 to the first relief pressure P1 is set in advance as a judgment value, and the judgment value is switched to the above. Compared with the actual change amount of the engine speed NE when a command to that effect is transmitted, if the change amount is smaller than the determination value, an abnormality has occurred in the hydraulic control mechanism 50 based on this change amount. It can also be determined.

  In the above embodiment, when a command for switching the relief pressure PX from the first relief pressure P1 to the second relief pressure P2 larger than this is transmitted to the hydraulic control mechanism 50, the engine load (fuel injection amount) Alternatively, the abnormality of the hydraulic control mechanism 50 is determined based on whether or not the intake air amount has changed to the increasing side, but this can be changed as follows, for example. That is, when a command for switching the relief pressure PX from the first relief pressure P1 to the second relief pressure P2 larger than this is transmitted to the hydraulic control mechanism 50, the engine load (fuel injection amount or intake air amount) is transmitted. It is also possible to determine abnormality of the hydraulic control mechanism 50 on the basis of whether or not the increase amount of) is equal to or greater than a predetermined determination value. In this case, when the increase amount of the engine load is greater than or equal to the determination value, it is determined that no abnormality has occurred in the hydraulic control mechanism 50. Conversely, when the increase amount of the engine load is less than the determination value, the abnormality of the control mechanism 50 has occurred. Is determined to have occurred.

In the above-described embodiment, the switching valve 52 that opens when energized is used, but a valve that opens when not energized can be used instead.
In the above embodiment, an electromagnetic valve is employed as the switching valve 52, but a switching valve that is driven by hydraulic pressure, negative pressure, or the like may be employed instead.

  In the above embodiment, the position of the sleeve 57 relative to the housing 55 is operated based on the force applied to the sleeve 57 by the lubricating oil in the switching chamber 57d. However, the configuration for this operation is the same as in the above embodiment. However, the configuration is not limited to those exemplified above. For example, an electric actuator for the sleeve 57 can be provided, and the position of the sleeve 57 can be changed through control of the actuator.

  In the above embodiment, the hydraulic pressure control mechanism 50 that can switch the relief pressure PX to the two stages of the first relief pressure P1 and the second relief pressure P2 for each part of the engine 10 is provided. As long as the relief pressure P1 and the second relief pressure P2 can be selected, the switching stage of the supply hydraulic pressure P is not limited to two stages. For example, as the hydraulic control mechanism 50, one that switches the relief pressure PX to three or more stages, or one that continuously changes the relief pressure PX can be adopted.

  In the above embodiment, as the hydraulic control mechanism 50, the one that sets the relief pressure PX to the first relief pressure P1 or the second relief pressure P2 by operating the position of the sleeve 57 with respect to the housing 55 is adopted, but the relief pressure PX The configuration for switching between is not limited to this. For example, the relief pressure PX can be switched by providing two pressure regulating valves with different control pressures in the hydraulic control mechanism 50 and selecting one of them.

  After all, the present invention can be applied to any supply device as long as it is a lubricating oil supply device that controls the setting of the relief pressure based on the engine operating state, and the configuration of the internal combustion engine is also possible. The configuration is not limited to the configuration exemplified in the above embodiment. And, as long as it is an embodiment of the invention within a range that satisfies this condition, the effects according to the above embodiment can be achieved in any case.

1 is a configuration diagram schematically showing a configuration of an internal combustion engine provided with the device according to an embodiment of the invention that embodies a lubricating oil supply device for an internal combustion engine according to the present invention. The block diagram which shows typically the structure of the hydraulic control mechanism about the lubricating oil supply apparatus of the embodiment. The schematic diagram which shows the operation | movement aspect of the hydraulic control mechanism about the lubrication supply apparatus of the same embodiment hydraulic control mechanism.

(A) The figure when a sleeve is a 1st movable position and supply hydraulic pressure is less than 1st relief pressure.
(B) The figure when a sleeve is a 1st movable position and supply hydraulic pressure is more than 1st relief pressure.
The schematic diagram which shows the operation | movement aspect of the hydraulic control mechanism about the lubrication supply apparatus of the same embodiment hydraulic control mechanism.

(A) The figure when a sleeve is a 2nd movable position and supply hydraulic pressure is less than 2nd relief pressure.
(B) The figure when a sleeve is a 2nd movable position and supply hydraulic pressure is more than 2nd relief pressure.
The graph which shows an example of the relationship between an engine speed and supply hydraulic pressure about the control aspect of supply hydraulic pressure by the lubricating oil supply apparatus of the embodiment. The flowchart which shows the process sequence about the "supply hydraulic pressure control process" performed by the electronic control apparatus of the embodiment. The flowchart which shows the process sequence about "the low voltage | pressure side abnormality determination process" performed by the electronic controller of the embodiment. The flowchart which shows the process sequence about "the high voltage | pressure side abnormality determination process" performed by the electronic controller of the embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Engine, 20 ... Engine main body, 21 ... Cylinder block, 22 ... Cylinder, 23 ... Piston, 24 ... Connecting rod, 25 ... Crankshaft, 26 ... Injector, 30 ... Combustion chamber, 40 ... Lubricating oil supply apparatus, 41 ... Oil pan, 42 ... supply passage, 43 ... oil pump, 44 ... oil strainer, 45 ... oil filter, 50 ... hydraulic control mechanism, 51 ... relief valve (hydraulic control valve), 52 ... switching valve (switching valve), 53 ... Relief passage (control passage), 54 ... Switching valve passage (movable passage), 55 ... Housing (valve body), 55a ... Bottom wall, 55b ... Housing inlet (body inlet), 55c ... Housing outlet (body outlet), 55d ... switching port, 55e ... end face, 56 ... oil chamber, 56d ... spring, 57 ... sleeve (movable body), 57a ... bottom wall, 57 ... Sleeve inlet (movable inlet), 57c ... Sleeve outlet (movable outlet), 57d ... Switching chamber, 57e ... End face, 58 ... Piston (valve element), 59 ... Closure, 59a ... Main body, 59b ... Flange, 60 ... Electronic control device 61 ... Accelerator position sensor 62 ... Throttle position sensor 63 ... Crank position sensor 64 ... Air flow meter

Claims (9)

A hydraulic control mechanism controls the pressure of a supply passage for supplying lubricating oil to the lubrication part of the internal combustion engine by an engine-driven oil pump. The hydraulic control mechanism is supplied from the supply passage to the control mechanism. In a lubricating oil supply device for an internal combustion engine comprising a component that relieves the lubricating oil to a predetermined portion when the pressure of the lubricating oil exceeds a predetermined relief pressure,
A determination unit configured to determine whether or not an abnormality has occurred in the hydraulic control mechanism based on a change in an engine operation state when a command to switch the predetermined relief pressure is transmitted to the hydraulic control mechanism; A lubricating oil supply device for an internal combustion engine. The lubricating oil supply device for an internal combustion engine according to claim 1,
When the command to increase or decrease the predetermined relief pressure by a predetermined amount is transmitted to the hydraulic control mechanism, the determination means causes a change in engine load in accordance with the direction of the change in the relief pressure. And determining that an abnormality has occurred in the hydraulic pressure control mechanism based on the fact that there is no failure. The lubricating oil supply device for an internal combustion engine according to claim 1 or 2,
The determination means increases the engine load when a command for switching the predetermined relief pressure from the first relief pressure on the low pressure side to the second relief pressure on the high pressure side is transmitted to the hydraulic control mechanism. It is determined that an abnormality has occurred in the hydraulic control mechanism based on the fact that no oil has occurred. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 3,
The determination means reduces the engine load when a command to switch the predetermined relief pressure from the second relief pressure on the high pressure side to the first relief pressure on the low pressure side is transmitted to the hydraulic control mechanism. It is determined that an abnormality has occurred in the hydraulic control mechanism based on the fact that no oil has occurred. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 4,
The hydraulic control mechanism includes a hydraulic control valve that relieves the lubricating oil upstream of the oil pump based on the pressure of the lubricating oil discharged from the oil pump exceeding the predetermined relief pressure, The predetermined relief pressure is switched between the low-pressure side first relief pressure and the high-pressure side second relief pressure by the hydraulic control valve,
The hydraulic control valve sets the predetermined relief pressure to the first relief pressure when the operation state is maintained in the first operation state, and the operation state is maintained in the second operation state. Sometimes, the predetermined relief pressure is set to the second relief pressure. A lubricating oil supply apparatus for an internal combustion engine, characterized in that: The lubricating oil supply device for an internal combustion engine according to claim 5,
The determination means has no increase in engine load when a command for switching the predetermined relief pressure from the first relief pressure to the second relief pressure is transmitted to the hydraulic control mechanism. Based on the above, it is determined that the hydraulic control valve is stuck in the first operating state as an abnormality of the hydraulic control mechanism. The lubricating oil supply device for an internal combustion engine according to claim 5 or 6,
The determination means has no engine load reduction when a command to switch the predetermined relief pressure from the second relief pressure to the first relief pressure is transmitted to the hydraulic control mechanism. Based on this, it is determined that the hydraulic control valve is stuck in the second operating state as an abnormality of the hydraulic control mechanism. The lubricating oil supply device for an internal combustion engine according to any one of claims 5 to 7,
The hydraulic control mechanism includes a control passage connecting the upstream side and the downstream side of the oil pump in the supply passage, and the pressure of lubricating oil provided in the control passage and discharged from the oil pump is the predetermined relief. The hydraulic control valve that relieves lubricating oil to the upstream side of the oil pump based on exceeding the pressure, and a switching mechanism that operates the hydraulic control valve to switch the predetermined relief pressure. And
The hydraulic control valve includes a valve body in which an oil chamber for retaining lubricating oil is formed, a valve body that is provided in the oil chamber and moves relative to the valve body, and between the valve body and the valve body. And is configured to include a movable body that moves relative to these,
The valve main body includes a main body inlet that communicates the control passage on the downstream side of the oil pump and the oil chamber, and a main body outlet that communicates the control passage and the oil chamber on the upstream side of the oil pump. It is configured to include,
The movable body includes a movable inlet provided between the main body inlet and the oil chamber to communicate with the movable body, and a movable outlet provided between the main body outlet and the oil chamber to communicate these. And configured to move between a first movable position and a second movable position with respect to the valve body, and the first movable position and the second movable position. The state where the main body inlet and the movable inlet communicate with each other and the state where the main body outlet and the movable outlet communicate with each other are maintained.
The valve body is at least a first valve body range that is closer to the movable inlet as a position relative to the valve body, and a second valve body range that is further away from the movable inlet and more than this. Either a third valve body range that is separated from the movable inlet or a fourth valve body range that is further away from the movable inlet can be taken, regardless of the position of the movable body. When in the first valve body range, between the movable inlet and the movable outlet is cut off to block the flow of lubricating oil from the main body inlet to the main body outlet, and the movable body is When in the first movable position and when in the second valve body range, the movable inlet and the movable outlet are communicated to allow the lubricant to flow from the main body inlet to the main body outlet. And When the movable body is in the second movable position and in the third valve body range, the movable inlet and the movable outlet are shut off and lubricating oil from the main body inlet to the main body outlet is blocked. When the movable body is in the fourth valve body range when the movable body is in the second movable position, the movable inlet and the movable outlet are communicated with each other,
The hydraulic control valve sets the first operating state when the movable body is in the first movable position, and sets the second operating state when the movable body is in the second movable position. Is,
The switching mechanism is configured to switch the predetermined relief pressure between the first relief pressure and the second relief pressure by manipulating the position of the movable body. Lubricating oil supply device. The lubricating oil supply device for an internal combustion engine according to claim 8,
The switching mechanism includes a switching chamber provided in the hydraulic control valve so as to be partitioned from the oil body between the valve body and the movable body, and a movable branching from the control passage and connected to the switching chamber. Comprising a passage and a switching valve for controlling the supply mode of the lubricating oil from the control passage to the switching chamber via the movable passage,
The movable body is set to the first movable position based on the supply of the lubricating oil to the switching chamber through the movable passage, and the supply of the lubricating oil to the switching chamber is shut off. Based on the second movable position,
The hydraulic control valve is configured such that the predetermined relief pressure is set to the first relief pressure based on the movable body being maintained at the first movable position, and the movable body is moved to the second movable position. The predetermined relief pressure is set to the second relief pressure based on being maintained at
The determination means includes at least one of the valve body, the movable body, and the switching valve based on a change in engine operating state when a command to switch the predetermined relief pressure is transmitted to the hydraulic control mechanism. A lubricating oil supply device for an internal combustion engine, characterized by determining whether or not an abnormality has occurred.

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