JP2010236525A - 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 preventing a hydraulic pressure control mechanism from being diagnosed to be defective despite the fact that the mechanism is not defective. <P>SOLUTION: This lubricating oil supply device 40 of an internal combustion engine 10 includes an oil pan 41 for reserving the lubricating oil supplied to each lubrication portion of the engine 10, an oil pump 43 for sucking the lubricating oil from the oil pan 41, a supply passage 42 for supplying the lubricating oil discharged by the oil pump 43 to each lubrication portion of the engine 10, a hydraulic pressure control mechanism 50 for controlling the hydraulic pressure of the supply passage 42, and a diagnosing means for diagnosing the trouble of the hydraulic control mechanism 50. When the diagnosing means determines that a supply hydraulic pressure P is smaller than a determination value PA and air is sucked by the oil pump 43, it is prohibited that the diagnosing means determines that the supply hydraulic pressure P is lower than the determination value PA due to the trouble of the hydraulic pressure control mechanism 50. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a storage part for storing lubricating oil supplied to each lubricating part of the internal combustion engine, an oil pump for sucking the lubricating oil from the storing part, and the lubricating oil discharged from the oil pump to each lubricating part of the internal combustion engine. The present invention relates to a lubricating oil supply device for an internal combustion engine, which includes a supply passage for supplying to the engine and a hydraulic control mechanism for changing the hydraulic pressure of the supply passage.

  A conventional lubricating oil supply device for an internal combustion engine includes a lubricating oil reservoir, an oil pump, a lubricating oil supply passage for supplying lubricating oil discharged from the oil pump to each lubricating portion of the internal combustion engine, and a hydraulic pressure in the lubricating oil supply passage. And a hydraulic control valve that opens when a predetermined valve opening pressure is reached, and a part of the lubricating oil is returned to the lubricating oil reservoir through the hydraulic control valve. In addition, the hydraulic pressure supplied to each lubricating part of the internal combustion engine can be switched through a hydraulic control mechanism that includes a switching valve that controls the valve opening pressure of the hydraulic control valve and includes the hydraulic control valve and the switching valve. I am doing so.

  In the lubricating oil supply apparatus having such a configuration, an abnormality may occur in the hydraulic control mechanism, resulting in insufficient hydraulic pressure. In Patent Document 1, when the actual hydraulic pressure is different from the required hydraulic pressure, it is determined that an abnormality has occurred in the hydraulic control mechanism, and countermeasures are taken.

JP 2008-57356 A

  By the way, although the cause of the lack of hydraulic pressure in the supply passage may be considered other than the abnormality of the hydraulic control mechanism, only the abnormality of the hydraulic control mechanism is the cause of the lack of hydraulic pressure in the conventional lubricating oil supply device. An abnormality diagnosis is made based on the premise. For this reason, when a shortage of hydraulic pressure occurs due to an abnormality in the hydraulic control mechanism, it is determined that an abnormality has occurred in the mechanism even though the hydraulic control mechanism is in a normal state. Become. For example, in the case where the fail-safe operation of the internal combustion engine is performed based on the diagnosis that an abnormality has occurred in the hydraulic control mechanism, such a fail-safe operation is made unnecessary. A decrease in drivability is inevitable.

  The present invention has been made in view of such a situation, and an object of the present invention is to suppress the diagnosis that an abnormality has occurred even though the abnormality has not occurred in the hydraulic control mechanism. 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) According to the first aspect of the present invention, a reservoir that stores lubricating oil supplied to each lubrication site of the internal combustion engine, an oil pump that sucks up the lubricating oil from the reservoir, and an oil pump that discharges the lubricant. Lubricating oil supply for an internal combustion engine comprising a supply passage for supplying lubricating oil to each lubrication site of the internal combustion engine, a hydraulic control mechanism for controlling the hydraulic pressure of the supply passage, and diagnostic means for performing abnormality diagnosis on the hydraulic control mechanism In the apparatus, when the diagnosis means determines that the hydraulic pressure in the supply passage is smaller than a hydraulic pressure determination value and that the air suction of the oil pump is occurring, the supply passage is caused by an abnormality in the hydraulic control mechanism. The gist is to prohibit the determination that the oil pressure is below the oil pressure determination value.

  The cause of the shortage of the hydraulic pressure in the supply passage is considered to be air suction of the oil pump in addition to the abnormality of the hydraulic control mechanism. Accordingly, when it is confirmed that the oil pressure in the supply passage is insufficient, if it is also confirmed that the air suction of the oil pump is occurring, the lack of the oil pressure is not caused by an abnormality in the hydraulic control mechanism. I can say that.

  In view of the above, in the present invention, it is determined that the oil pressure in the supply passage is below the oil pressure determination value in the above manner, so that an abnormality occurs even though there is no abnormality in the hydraulic control mechanism. It is possible to suppress the diagnosis of the fact that it is being performed.

  (2) The invention described in claim 2 is a storage section that stores lubricating oil supplied to each lubrication site of the internal combustion engine, an oil pump that sucks up the lubricating oil from the storage section, and an oil pump that discharges the lubricating oil. Lubricating oil supply for an internal combustion engine comprising a supply passage for supplying lubricating oil to each lubrication site of the internal combustion engine, a hydraulic control mechanism for controlling the hydraulic pressure of the supply passage, and diagnostic means for performing abnormality diagnosis on the hydraulic control mechanism In the apparatus, the hydraulic control mechanism switches a pressure for relief of the lubricating oil in the supply passage between a first relief pressure on the low pressure side and a second relief pressure on the high pressure side. That there is a request to set the relief pressure of the hydraulic control mechanism to the second relief pressure, and that the hydraulic pressure in the supply passage is smaller than the second relief pressure as a hydraulic pressure judgment value, and When it is determined that air suction of the oil pump has occurred, it is prohibited to determine that the hydraulic pressure in the supply passage is below the second relief pressure due to an abnormality in the hydraulic control mechanism. This is the gist.

  The cause of the shortage of the hydraulic pressure in the supply passage is considered to be air suction of the oil pump in addition to the abnormality of the hydraulic control mechanism. Accordingly, when it is confirmed that the oil pressure in the supply passage is insufficient, if it is also confirmed that the air suction of the oil pump is occurring, the lack of the oil pressure is not caused by an abnormality in the hydraulic control mechanism. I can say that.

  In the present invention, in view of the above, since it is determined that the hydraulic pressure of the supply passage is below the second relief pressure with the above-described aspect, there is an abnormality although no abnormality has occurred in the hydraulic control mechanism. It can suppress that the diagnosis to the effect is made.

  (3) The invention according to claim 3 is a storage section for storing the lubricating oil supplied to each lubrication site of the internal combustion engine, an oil pump for sucking the lubricating oil from the storage section, and the oil pump for discharging the lubricating oil. Lubricating oil supply for an internal combustion engine comprising a supply passage for supplying lubricating oil to each lubrication site of the internal combustion engine, a hydraulic control mechanism for controlling the hydraulic pressure of the supply passage, and diagnostic means for performing abnormality diagnosis on the hydraulic control mechanism In the apparatus, the hydraulic control mechanism switches a pressure for relief of the lubricating oil in the supply passage between a first relief pressure on the low pressure side and a second relief pressure on the high pressure side. That there is a request to set the relief pressure of the hydraulic control mechanism to the first relief pressure, and that the hydraulic pressure in the supply passage is smaller than the first relief pressure as an oil pressure judgment value, and When it is determined that air suction of the oil pump has occurred, it is prohibited to determine that the hydraulic pressure in the supply passage is below the first relief pressure due to an abnormality in the hydraulic control mechanism It is said.

  The cause of the shortage of the hydraulic pressure in the supply passage is considered to be air suction of the oil pump in addition to the abnormality of the hydraulic control mechanism. Accordingly, when it is confirmed that the oil pressure in the supply passage is insufficient, if it is also confirmed that the air suction of the oil pump is occurring, the lack of the oil pressure is not caused by an abnormality in the hydraulic control mechanism. I can say that.

  In the present invention, in view of the above, since it is determined that the hydraulic pressure of the supply passage is below the first relief pressure with the above-described aspect, the abnormality is not caused in the hydraulic control mechanism. It can suppress that the diagnosis to the effect is made.

  (4) The invention described in claim 4 is a storage unit that stores lubricating oil supplied to each lubricating portion of the internal combustion engine, an oil pump that sucks up the lubricating oil from the storage unit, and the oil pump that discharges the lubricating oil. Lubricating oil supply for an internal combustion engine comprising a supply passage for supplying lubricating oil to each lubrication site of the internal combustion engine, a hydraulic control mechanism for controlling the hydraulic pressure of the supply passage, and diagnostic means for performing abnormality diagnosis on the hydraulic control mechanism The gist of the apparatus is that the diagnostic means prohibits execution of an abnormality diagnosis for the hydraulic control mechanism when it is determined that air suction of the oil pump has occurred.

  (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 diagnosis means is configured such that the oil pressure in the supply passage is less than the oil pressure determination value. The gist is to determine that the oil pressure in the supply passage is below the oil pressure judgment value due to the air suction when it is determined that the oil pump is small and that the air suction of the oil pump is occurring.

  (6) According to a sixth aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to any one of the first to fifth aspects, the diagnostic means is configured such that the oil level of the reservoir is determined from a level determination value. The gist is to determine that the air suction of the oil pump has occurred based on the low value.

  For oil pump air suction, this generally occurs because the oil level in the reservoir is too low. Therefore, as in the above-described invention, by determining whether or not the air suction of the oil pump has occurred based on the comparison result between the oil level and the level determination value, an appropriate one can be obtained as a result. Become.

  (7) The invention according to claim 7 is the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 6, wherein the diagnosis means is configured such that the oil pressure in the supply passage is less than the oil pressure determination value. The gist is to determine that an abnormality has occurred in the hydraulic control mechanism when it is determined that the oil is not sucked by the oil pump.

  The cause of the shortage of the hydraulic pressure in the supply passage is considered to be either the abnormality of the hydraulic control mechanism or the air suction of the oil pump as described above. When no decrease in level is confirmed, it can be said that the lack of hydraulic pressure is due to an abnormality in the hydraulic control mechanism.

  In view of the above, in the above invention, since it is determined that the hydraulic pressure of the supply passage is below the hydraulic pressure determination value with the above aspect, it is possible to accurately determine that an abnormality has occurred in the hydraulic control mechanism. Will be able to.

  (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 first to seventh aspects, the diagnosis means is configured such that the hydraulic pressure in the supply passage is lower than a hydraulic pressure determination value. The gist of the present invention is to perform a fail-safe operation of the internal combustion engine when it is determined that the oil pump is small and air suction of the oil pump is not occurring.

  (9) The invention according to claim 9 is the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 8, wherein the hydraulic control mechanism relieves the lubricating oil in the supply passage. Is switched between a first relief pressure on the low pressure side and a second relief pressure on the high pressure side, and the diagnosis means indicates that the oil pressure in the supply passage is smaller than a hydraulic pressure judgment value and the oil pump The gist is that when it is determined that no air suction has occurred, it is determined that an abnormality has occurred that makes it impossible to switch the relief pressure from the first relief pressure to the second relief pressure in the hydraulic control mechanism. Yes.

  (10) The invention according to claim 10 is the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 9, wherein the hydraulic pressure control mechanism is configured to apply pressure of lubricating oil discharged from an oil pump. Includes a hydraulic control valve that relieves lubricating oil to the upstream side of the oil pump based on exceeding a predetermined relief pressure, and the predetermined relief pressure and the second relief pressure are reduced 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 The gist is that when the second operating state is maintained, the predetermined relief pressure is set to the second relief pressure.

  (11) According to an eleventh aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the tenth aspect, the hydraulic control mechanism connects an upstream side and a downstream side of the oil pump in the supply passage. A control passage, and the hydraulic control valve provided in the control passage and configured to relieve 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. 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 a movable body that is provided between the valve body and the valve body and moves relative to the valve body. In The valve body includes a main body inlet communicating the control passage on the downstream side of the oil pump and the oil chamber, and a main body outlet communicating the control passage and the oil chamber on the upstream side of the oil pump. The movable body is provided between the main body inlet and the oil chamber, and is provided between the main body outlet and the oil chamber. And a movable outlet that communicates with each other, and moves between a first movable position and a second movable position with respect to the valve body, and the first Maintaining the state in which the main body inlet and the movable inlet are in communication with each other and the state in which the main body outlet and the movable outlet are in communication when the movable position and the second movable position are both. The valve body is positioned relative to the valve body. And at least the first valve body range near the movable inlet and the second valve body range further away from the movable inlet and further away from the movable inlet. Either the third valve body range or the fourth valve body range that is further away from the movable inlet than the third valve body range can be taken, and is in the first valve body range regardless of the position of the movable body. Sometimes when the movable inlet and the movable outlet are blocked to block 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 In the second movable position And when it is within the third valve body range, the gap 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 When the body is in the second movable position and in the fourth valve body range, the movable inlet communicates with the movable outlet. The first operating state is the first movable position, the second operating state is the movable body is the second movable position, and the switching mechanism is the movable The gist is that the predetermined relief pressure is switched between the first relief pressure and the second relief pressure by manipulating the position of the body.

  (12) According to a twelfth aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the eleventh aspect, the switching mechanism includes the oil control valve between the valve body and the movable body. 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. Said predetermined relief pressure based on being maintained The first relief pressure is set, and the predetermined relief pressure is set to the second relief pressure based on the movable body being maintained at the second movable position. When it is determined that the oil pressure in the supply passage is smaller than the oil pressure determination value and that air suction of the oil pump has not occurred, the supply due to at least one abnormality of the valve body, the movable body, and the switching valve The gist is that it is determined that the hydraulic pressure of the passage is below the hydraulic pressure determination value.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a configuration diagram schematically showing a configuration of an internal combustion engine provided with the device according to a first embodiment that embodies an internal combustion engine lubricant oil supply device 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 1st hydraulic control mechanism abnormality diagnosis process" performed by the electronic controller of the embodiment. The flowchart which shows the process sequence of the "2nd hydraulic-control-mechanism abnormality diagnosis process" performed by the electronic controller about 2nd Embodiment which actualized the lubricating oil supply apparatus of the internal combustion engine concerning this invention. The flowchart which shows the process sequence of the "3rd hydraulic-control-mechanism abnormality diagnosis process" performed by the electronic controller about 3rd Embodiment which actualized the lubricating oil supply apparatus of the internal combustion engine concerning this invention.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS.
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 pressure is set to the second relief pressure (hereinafter “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 on the basis that the supply hydraulic pressure P exceeds the second relief pressure P2, so that the lubricating oil discharged from the oil pump 43 is the same. Relief to the upstream side of the pump 43.

  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 determines the engine operating state and the vehicle based on signals from various sensors including an accelerator position sensor 61, a throttle position sensor 62, a crank position sensor 63, an air flow meter 64, a hydraulic pressure sensor 65, and an oil level sensor 66. For example, the following control is performed after grasping the driving state and the driver's request. 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. The hydraulic sensor 65 outputs a signal corresponding to the supplied hydraulic pressure P. The oil level sensor 66 outputs a signal corresponding to the oil level in the oil pan 41 (hereinafter referred to as “oil level L”).

  Here, in the hydraulic pressure control, the hydraulic pressure control mechanism 50 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 portion of the engine body 20. Specifically, when the engine speed NE is in the low rotation range or the middle rotation range, the operation state of the hydraulic control mechanism 50 is set to the low pressure mode through the control of the switching valve 52. At this time, the relief pressure PX is set to the first relief pressure P1 on the low pressure side. On the other hand, when the engine speed NE is in the high rotation region, the operation state of the hydraulic control mechanism 50 is set to the high pressure mode through the control of the switching valve 52. At this time, the relief pressure PX is set to the second relief pressure P2 on the high pressure side.

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 oil 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 oil pressure P and the spring 56a. 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 56a. 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 56a. 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 56a. 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” that defines the specific processing procedure of 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, in the hydraulic control mechanism 50 having the above-described configuration, an abnormality that cannot be switched to the high-pressure mode occurs due to an abnormality in fixing of the relief valve 51 or the switching valve 52, and the supply hydraulic pressure P may be insufficient. That is, when the engine rotation speed NE is in the high rotation region, there may be an abnormality in which the supply hydraulic pressure P cannot be increased to the pressure required in this operating state. In this case, there is a high possibility that the engine 10 will burn.

  Here, as an abnormality of the hydraulic control mechanism 50, a command to switch the relief pressure PX from the first relief pressure P1 to the second relief pressure P2 due to the occurrence of sticking to at least one of the relief valve 51 and the switching valve 52. In this case, the hydraulic control mechanism 50 is maintained in the low pressure mode despite the above. Separately from this, in a state where the hydraulic control mechanism 50 is maintained in the high pressure mode based on a request for setting the relief pressure PX to the second relief pressure P2, at least one of the relief valve 51 and the switching valve 52 is selected. There is also a case where the hydraulic control mechanism 50 is unintentionally switched to the low pressure mode due to an abnormality. Furthermore, although the operating state of the hydraulic control mechanism 50 is maintained in the high pressure mode, the function of relieving the lubricating oil based on the supply hydraulic pressure P exceeding the second relief pressure P2 for some reason is maintained. In this case, the supply hydraulic pressure P is insufficient. Even if any abnormality occurs, the possibility of causing the engine 10 to burn-in due to the shortage of the supply hydraulic pressure P as described above is relatively high.

  Therefore, in order to cope with such a problem, the engine 10 performs an abnormality diagnosis of the hydraulic control mechanism 50. When an abnormality of the hydraulic control mechanism 50 is determined through this abnormality diagnosis, the operation mode of the engine 10 is shifted from the normal mode to a fail safe mode in which the engine load is limited to protect the engine 10.

  On the other hand, in addition to the abnormality of the hydraulic control mechanism 50 described above, the cause of the shortage of the supply hydraulic pressure P includes air when the oil pump 43 sucks lubricating oil due to a decrease in the oil level L in the oil pan 41. So-called air sucking that sucks in is also conceivable.

  As described above, the cause of insufficient hydraulic pressure in the supply passage 42 is an abnormality of the hydraulic control mechanism 50 and air suction of the oil pump 43. However, in the conventional lubricating oil supply apparatus 40, only an abnormality of the hydraulic control mechanism 50 is hydraulic. Abnormal diagnosis has been made on the assumption that it is the cause of the shortage. For this reason, when a hydraulic pressure shortage occurs due to an abnormality in the hydraulic control mechanism 50, it is determined that an abnormality has occurred in the mechanism 50 even though the hydraulic control mechanism 50 is in a normal state. It becomes like this.

  Possible causes of the shortage of the supply hydraulic pressure P in the supply passage 42 include air suction of the oil pump 43 in addition to the abnormality of the hydraulic control mechanism 50. Therefore, when it is confirmed that the oil pump 43 is sucking air when the decrease in the hydraulic pressure in the supply passage 42 is confirmed, the shortage of the supply hydraulic pressure P is caused by an abnormality in the hydraulic control mechanism 50. It can be said that this is not caused by the air suction of the oil pump 43.

  Accordingly, in the present embodiment, in view of the above, when it is determined that the oil pressure in the supply passage 42 is smaller than the oil pressure determination value and the air suction of the oil pump 43 occurs, the supply passage 42 It is determined that the hydraulic pressure is below the hydraulic pressure determination value.

  That is, when the pressure of the supply passage 42 is smaller than the hydraulic pressure determination value, there is a possibility that an abnormality of the hydraulic control mechanism 50 has occurred, but there is still a possibility that it is caused by air suction of the oil pump 43. If the air suction of the oil pump 43 does not occur when the pressure in the supply passage 42 is smaller than the hydraulic pressure determination value, it is determined that the shortage of the pressure is caused by an abnormality in the hydraulic control mechanism 50. For example, it is determined that the oil pump 43 is caused by air suction.

  As a result, when the supply hydraulic pressure P is insufficient due to air suction, the determination to that effect is made appropriately, so that an abnormality has occurred even though the hydraulic control mechanism 50 has not failed. It will be suppressed that the diagnosis of this is made.

  With reference to FIG. 7, the content of the “first hydraulic control mechanism abnormality diagnosis process” that defines a specific processing procedure for such abnormality diagnosis 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 the abnormality diagnosis process, first, in step S210, based on the detection result of the hydraulic sensor 65, it is determined whether or not the supply hydraulic pressure P is smaller than a hydraulic pressure determination value (hereinafter referred to as “determination value PA”). The determination value PA is a value for determining whether there is a risk of seizing in the engine high load operation state, and is set in advance through a test or the like. Here, a value between the first relief pressure P1 and the second relief pressure P2 is set as the determination value PA.

  When it is determined in step S210 that the supply hydraulic pressure P is greater than or equal to the determination value PA, that is, when it is estimated that there is no shortage of the supply hydraulic pressure P in the supply passage 42, this process is temporarily terminated. On the other hand, when it is determined that the supply oil pressure P is smaller than the determination value PA, that is, when it is estimated that the supply oil pressure P is insufficient in the supply passage 42, the oil level in the oil pan 41 in the next step S220. It is determined whether L is lower than a level determination value (hereinafter referred to as “determination value LX”). Specifically, based on the detection result of the oil level sensor 66, it is determined whether or not the oil level L is lower than the determination value LX. The determination value LX is a value for determining that the oil level L has decreased to a level that would cause the air suction of the oil pump 43, that is, the oil level L is lower than the suction port of the oil pump 43. It is a value for determining the value, and is set in advance through a test or the like.

  When it is determined in step S220 that the oil level L is lower than the determination value LX, that is, when it is estimated that the air suction of the oil pump 43 has occurred, the shortage of the supply hydraulic pressure P determined in step S210 is the oil level. It is determined that this is due to a decrease in L. Then, based on the fact that the supply hydraulic pressure P is reduced due to the air suction of the oil pump 43, the execution of the abnormality diagnosis for the hydraulic control mechanism 50 is prohibited in step S250, and this processing is temporarily ended.

  On the other hand, when it is determined in step S220 that the oil level L is equal to or higher than the determination value LX, that is, when it is estimated that the air suction of the oil pump 43 has not occurred, the supply hydraulic pressure determined in step S210. It is determined that the lack of P is due to an abnormality in the hydraulic control mechanism 50. That is, it is determined that an abnormality has occurred in the hydraulic control mechanism 50.

  In the next step S230, data indicating that an abnormality has occurred in the hydraulic control mechanism 50 is stored in the memory, and then in step S240, the operation mode of the engine 10 is shifted to the fail safe mode. In this fail-safe mode, the upper limit of the engine load (intake air amount and fuel injection amount) is set smaller than in the normal operation mode, and the engine speed NE is prevented from becoming high.

  As described above, in the abnormality diagnosis process, there is a possibility that an abnormality has occurred in the hydraulic control mechanism 50 based on the fact that the supply hydraulic pressure P is smaller than the determination value PA, that is, the supply hydraulic pressure P is insufficient. Based on whether or not the air suction of the oil pump 43 has occurred, it is confirmed whether or not the shortage of the supplied hydraulic pressure P is caused by an abnormality of the hydraulic control mechanism 50. .

  When the supply hydraulic pressure P is insufficient and the air suction of the oil pump 43 does not occur, an abnormality has occurred in the hydraulic control mechanism 50 based on this, and the supply hydraulic pressure P due to this abnormality. It is determined that a shortage has occurred. On the other hand, when the supply hydraulic pressure P is insufficient and the air suction of the oil pump 43 does not occur, abnormality diagnosis of the hydraulic control mechanism 50 is prohibited based on this, and the supply hydraulic pressure P is insufficient. It is determined that the error is not caused by the abnormality.

According to the lubricating oil supply device for an internal combustion engine of the present embodiment, the following effects can be obtained.
(1) In this embodiment, when it is determined that the supply hydraulic pressure P is smaller than the determination value PA and the air suction of the oil pump 43 has occurred, the supply hydraulic pressure P is determined due to the abnormality of the hydraulic control mechanism 50. It is prohibited to determine that the value is below the value PA. Accordingly, it is possible to suppress a diagnosis that an abnormality has occurred even though no abnormality has occurred in the hydraulic control mechanism 50.

  (2) In the present embodiment, it is determined whether or not the air suction of the oil pump 43 occurs based on the comparison result between the oil level L and the determination value LX. As a result, an appropriate one can be obtained as a result.

  (3) In this embodiment, when it is determined that the supply hydraulic pressure P is smaller than the determination value PA and the air suction of the oil pump 43 has not occurred, it is determined that an abnormality has occurred in the hydraulic control mechanism 50. ing. This makes it possible to accurately determine that an abnormality has occurred in the hydraulic control mechanism 50.

(Second Embodiment)
A second embodiment of the present invention will be described with reference to FIG. In the first embodiment, it is determined that an abnormality has occurred in the hydraulic control mechanism 50 when the supply hydraulic pressure P is smaller than the determination value PA and the air suction of the oil pump 43 has not occurred. . That is, when the supply oil pressure P is smaller than the determination value PA, there is a possibility that an abnormality has occurred in the oil pressure control mechanism 50, but on the other hand, the supply oil pressure P is insufficient due to air suction of the oil pump 43. Therefore, the final abnormality diagnosis result should be set after confirming through the comparison between the oil level L and the judgment value LX which is caused by the shortage of the supply hydraulic pressure P. I have to.

  Here, as a method for determining the possibility of abnormality of the hydraulic control mechanism 50, the following method is also included in addition to the method according to the first embodiment. That is, even when there is a request to set the relief pressure PX to the second relief pressure P2, when the supply oil pressure P is smaller than the second relief pressure P2, an abnormality may still occur in the hydraulic control mechanism 50. There is sex. However, in this case as well, there is still a possibility that the shortage of the supply hydraulic pressure P is caused by the air suction of the oil pump 43, so that there is no abnormality in the hydraulic control mechanism 50. In order to suppress the diagnosis that an abnormality has occurred, it is required to confirm which is the cause of the lack of the supply hydraulic pressure P.

  In the present embodiment, as a method for determining the possibility of abnormality of the hydraulic control mechanism 50, the above-described method different from that according to the first embodiment is adopted, and then the hydraulic control mechanism 50 is used. In order to prevent misdiagnosis of the following, the following configuration is adopted.

  That is, it is determined that there is a request to set the relief pressure PX to the second relief pressure P2, the supply hydraulic pressure P is smaller than the second relief pressure P2, and air suction of the oil pump 43 occurs. When this is done, it is determined that the supply hydraulic pressure P is below the second relief pressure P2 due to the suction of the air.

  As a result, when the supply hydraulic pressure P is insufficient due to air suction, the determination to that effect is made appropriately, so that an abnormality has occurred even though the hydraulic control mechanism 50 has not failed. It will be suppressed that the diagnosis of this is made.

  The present embodiment is different from the first embodiment in the above points. Specifically, the determination process in step S210 of the “first hydraulic control mechanism abnormality diagnosis process” of the first embodiment is described below. Is replaced with a process for determining whether or not the supply hydraulic pressure P is smaller than the second relief pressure P2, and an abnormality diagnosis of the hydraulic control mechanism 50 is performed by a new abnormality diagnosis process after the replacement. In addition, about the other structure, the structure substantially the same as the said 1st Embodiment is employ | adopted.

  With reference to FIG. 8, the content of the “second hydraulic control mechanism abnormality diagnosis process” that defines a specific processing procedure of the abnormality diagnosis process will be described. This process is repeatedly executed at predetermined control intervals by the electronic control unit 60 during operation of the engine 10. Moreover, the part enclosed with the broken line in the figure corresponds to a different point from 1st Embodiment.

  In the abnormality diagnosis process, first, in step S310, whether there is a request for setting the relief pressure PX to the second relief pressure P2, that is, a command for maintaining the hydraulic control mechanism 50 in the high pressure mode is sent to the mechanism 50. It is determined whether or not it is being transmitted.

  When it is determined that there is a request to set the relief pressure PX to the second relief pressure P2, it is determined in the next step S320 whether the supply oil pressure P is smaller than the second relief pressure P2. Regarding this determination, when the relief pressure PX is appropriately switched from the first relief pressure P1 to the second relief pressure P2, it is considered that the supply hydraulic pressure P reaches the second relief pressure P2 with a delay relative to this. It is done after that. That is, the supply hydraulic pressure P is maintained at the first level even if the hydraulic control mechanism 50 is operating normally until a predetermined period elapses after the request for the relief pressure PX is switched from the first relief pressure P1 to the second relief pressure P2. Since the pressure does not reach 2 relief pressure P2, the determination process of step S320 is performed after confirming the passage of the predetermined period.

  When it is determined in step S320 that the supply oil pressure P is equal to or greater than the second relief pressure P2, that is, when it is estimated that the supply oil pressure P is not insufficient in the supply passage 42, this process is temporarily ended. To do. On the other hand, when it is determined that the supply hydraulic pressure P is smaller than the second relief pressure P2, that is, when it is estimated that the supply hydraulic pressure P is insufficient in the supply passage 42, the next step S330 is performed in the oil pan 41. It is determined whether the oil level L is lower than the determination value LX. The subsequent processing is performed in accordance with the processing in the first embodiment.

  As described above, in the abnormality diagnosis process, there is a request for setting the relief pressure PX to the second relief pressure P2, and the supply hydraulic pressure P is smaller than the second relief pressure P2, that is, the supply hydraulic pressure P is insufficient. Based on what has occurred, it is determined that there is a possibility that an abnormality has occurred in the hydraulic control mechanism 50, and based on whether or not air suction of the oil pump 43 has occurred, the shortage of the supplied hydraulic pressure P is determined. It is confirmed whether or not it is caused by an abnormality of the hydraulic control mechanism 50.

  When the supply hydraulic pressure P is insufficient and the air suction of the oil pump 43 does not occur, an abnormality has occurred in the hydraulic control mechanism 50 based on this, and the supply hydraulic pressure P due to this abnormality. It is determined that a shortage has occurred. On the other hand, when the supply hydraulic pressure P is insufficient and the air suction of the oil pump 43 does not occur, abnormality diagnosis of the hydraulic control mechanism 50 is prohibited based on this, and the supply hydraulic pressure P is insufficient. It is determined that the error is not caused by the abnormality.

Note that the lubricating oil supply device 40 of this embodiment can also achieve the effects according to the effects (1) to (3) of the previous first embodiment.
(Third embodiment)
A third embodiment of the present invention will be described with reference to FIG. In the first embodiment, it is determined that an abnormality has occurred in the hydraulic control mechanism 50 when the supply hydraulic pressure P is smaller than the determination value PA and the air suction of the oil pump 43 has not occurred. . That is, when the supply oil pressure P is smaller than the determination value PA, there is a possibility that an abnormality has occurred in the oil pressure control mechanism 50, but on the other hand, the supply oil pressure P is insufficient due to air suction of the oil pump 43. Therefore, the final abnormality diagnosis result should be set after confirming through the comparison between the oil level L and the judgment value LX which is caused by the shortage of the supply hydraulic pressure P. I have to.

  Here, as a method for determining the possibility of abnormality of the hydraulic control mechanism 50, the following method is also included in addition to the method according to the first embodiment. That is, even when there is a request for setting the relief pressure PX to the first relief pressure P1, when the supply hydraulic pressure P is smaller than the first relief pressure P1, an abnormality may occur in the hydraulic control mechanism 50. There is sex. However, in this case as well, there is still a possibility that the shortage of the supply hydraulic pressure P is caused by the air suction of the oil pump 43, so that there is no abnormality in the hydraulic control mechanism 50. In order to suppress the diagnosis that an abnormality has occurred, it is required to confirm which is the cause of the lack of the supply hydraulic pressure P.

  In the present embodiment, as a method for determining the possibility of abnormality of the hydraulic control mechanism 50, the above-described method different from that according to the first embodiment is adopted, and then the hydraulic control mechanism 50 is used. In order to prevent misdiagnosis of the following, the following configuration is adopted.

  That is, it is determined that there is a request to set the relief pressure PX to the first relief pressure P1, the supply hydraulic pressure P is smaller than the first relief pressure P1, and the oil pump 43 is sucking air. When this is done, it is determined that the supply hydraulic pressure P is below the first relief pressure P1 due to the suction of the air.

  As a result, when the supply hydraulic pressure P is insufficient due to air suction, the determination to that effect is made appropriately, so that an abnormality has occurred even though the hydraulic control mechanism 50 has not failed. It will be suppressed that the diagnosis of this is made.

  The present embodiment is different from the first embodiment in the above points. Specifically, the determination process in step S210 of the “first hydraulic control mechanism abnormality diagnosis process” of the first embodiment is described below. Is replaced with a process for determining whether or not the supply hydraulic pressure P is smaller than the first relief pressure P1, and an abnormality diagnosis for the hydraulic control mechanism 50 is performed by the new abnormality diagnosis process after the replacement. In addition, about the other structure, the structure substantially the same as the said 1st Embodiment is employ | adopted.

  With reference to FIG. 9, the content of the “third hydraulic control mechanism abnormality diagnosis process” that defines a specific processing procedure of the abnormality diagnosis process will be described. This process is repeatedly executed at predetermined control intervals by the electronic control unit 60 during operation of the engine 10. Moreover, the part enclosed with the broken line in the figure corresponds to a different point from 1st Embodiment.

  In the abnormality diagnosis process, first, in step S410, whether or not there is a request for setting the relief pressure PX to the first relief pressure P1, that is, a command for maintaining the hydraulic control mechanism 50 in the high pressure mode is sent to the mechanism 50. It is determined whether or not it is being transmitted.

  When it is determined that there is a request to set the relief pressure PX to the first relief pressure P1, it is determined in the next step S420 whether the supply hydraulic pressure P is smaller than the first relief pressure P1. This determination is made after taking into account that the supply hydraulic pressure P reaches the first relief pressure P1 with a delay when the relief pressure PX is appropriately set to the first relief pressure P1. That is, until the predetermined period elapses after the request for the relief pressure PX is set to the first relief pressure P1, the supplied hydraulic pressure P is reduced to the first relief pressure P1 even if the hydraulic control mechanism 50 is operating normally. Since it does not reach, the determination process of step S420 is performed after confirming the passage of the predetermined period.

  When it is determined in step S420 that the supply oil pressure P is equal to or greater than the first relief pressure P1, that is, when it is estimated that the supply oil pressure P is not insufficient in the supply passage 42, this process is temporarily terminated. To do. On the other hand, when it is determined that the supply hydraulic pressure P is smaller than the first relief pressure P1, that is, when it is estimated that the supply hydraulic pressure P is insufficient in the supply passage 42, the next step S430 is performed in the oil pan 41. It is determined whether the oil level L is lower than the determination value LX. The subsequent processing is performed in accordance with the processing in the first embodiment.

  As described above, in the abnormality diagnosis process, there is a request for setting the relief pressure PX to the first relief pressure P1, and the supply hydraulic pressure P is smaller than the first relief pressure P1, that is, the supply hydraulic pressure P is insufficient. Based on what has occurred, it is determined that there is a possibility that an abnormality has occurred in the hydraulic control mechanism 50, and based on whether or not air suction of the oil pump 43 has occurred, the shortage of the supplied hydraulic pressure P is determined. It is confirmed whether or not it is caused by an abnormality of the hydraulic control mechanism 50.

  When the supply hydraulic pressure P is insufficient and the air suction of the oil pump 43 does not occur, an abnormality has occurred in the hydraulic control mechanism 50 based on this, and the supply hydraulic pressure P due to this abnormality. It is determined that a shortage has occurred. On the other hand, when the supply hydraulic pressure P is insufficient and the air suction of the oil pump 43 does not occur, abnormality diagnosis of the hydraulic control mechanism 50 is prohibited based on this, and the supply hydraulic pressure P is insufficient. It is determined that the error is not caused by the abnormality.

Note that the lubricating oil supply device 40 of this embodiment can also achieve the effects according to the effects (1) to (3) of the previous first embodiment.
(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 first embodiment, a value between the first relief pressure P1 and the second relief pressure P2 is set as the determination value PA. Instead, a value smaller than the first relief pressure P1 is set. You can also. Alternatively, based on the engine speed NE and the engine load, a supply hydraulic pressure P that is optimal for the current operating state can be calculated and set as the determination value PA.

  In each of the above embodiments, it is determined whether or not the air suction of the oil pump 43 has occurred through a comparison between the oil level L and the determination value LX. The configuration is not limited to this. For example, it can be determined that the air suction of the oil pump 43 has occurred based on the fact that the discharge amount of the oil pump 43 has decreased below a predetermined amount.

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

  In each of the above embodiments, 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 above embodiment. However, the configuration is not limited to that illustrated in FIG. 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 each of the above embodiments, 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 first 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 each of the above embodiments, 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. The configuration for switching PX 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 as appropriate.

  -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 rotation speed, 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.

  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, 56a ... 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 DESCRIPTION OF SYMBOLS Electronic control device 61 ... Accelerator position sensor 62 ... Throttle position sensor 63 ... Crank position sensor 64 ... Air flow meter 65 ... Hydraulic sensor 66 ... Oil level sensor

Claims (12)

A reservoir for storing lubricating oil to be supplied to each lubricating part of the internal combustion engine, an oil pump for sucking up the lubricating oil from the storing part, and a lubricating oil discharged from the oil pump to each lubricating part of the internal combustion engine In a lubricating oil supply device for an internal combustion engine comprising a supply passage, a hydraulic control mechanism that controls the hydraulic pressure of the supply passage, and a diagnostic unit that performs an abnormality diagnosis on the hydraulic control mechanism,
When the diagnosis means determines that the oil pressure in the supply passage is smaller than the oil pressure determination value and that the air suction of the oil pump is occurring, the oil pressure in the supply passage is caused by an abnormality in the oil pressure control mechanism. A lubricating oil supply device for an internal combustion engine, characterized in that it is prohibited to determine that it is below a hydraulic pressure determination value. A reservoir for storing lubricating oil to be supplied to each lubricating part of the internal combustion engine, an oil pump for sucking up the lubricating oil from the storing part, and a lubricating oil discharged from the oil pump to each lubricating part of the internal combustion engine In a lubricating oil supply device for an internal combustion engine comprising a supply passage, a hydraulic control mechanism that controls the hydraulic pressure of the supply passage, and a diagnostic unit that performs an abnormality diagnosis on the hydraulic control mechanism,
The hydraulic control mechanism switches a pressure for relief of the lubricating oil in the supply passage between a first relief pressure on the low pressure side and a second relief pressure on the high pressure side,
The diagnosis means that there is a request to set the relief pressure of the hydraulic control mechanism to a second relief pressure, that the hydraulic pressure of the supply passage is smaller than a second relief pressure as a hydraulic pressure judgment value, and the oil pump When it is determined that air suction is occurring, it is prohibited to determine that the hydraulic pressure in the supply passage is below the second relief pressure due to an abnormality in the hydraulic control mechanism. A lubricating oil supply device for an internal combustion engine. A reservoir for storing lubricating oil to be supplied to each lubricating part of the internal combustion engine, an oil pump for sucking up the lubricating oil from the storing part, and a lubricating oil discharged from the oil pump to each lubricating part of the internal combustion engine In a lubricating oil supply device for an internal combustion engine comprising a supply passage, a hydraulic control mechanism that controls the hydraulic pressure of the supply passage, and a diagnostic unit that performs an abnormality diagnosis on the hydraulic control mechanism,
The hydraulic control mechanism switches a pressure for relief of the lubricating oil in the supply passage between a first relief pressure on the low pressure side and a second relief pressure on the high pressure side,
The diagnosis means that there is a request to set the relief pressure of the hydraulic control mechanism to the first relief pressure, that the hydraulic pressure in the supply passage is smaller than the first relief pressure as a hydraulic pressure judgment value, and the oil pump When it is determined that the air suction is occurring, it is prohibited to determine that the hydraulic pressure in the supply passage is below a first relief pressure due to an abnormality in the hydraulic control mechanism. Engine lubricant supply device. A reservoir for storing lubricating oil to be supplied to each lubricating part of the internal combustion engine, an oil pump for sucking up the lubricating oil from the storing part, and a lubricating oil discharged from the oil pump to each lubricating part of the internal combustion engine In a lubricating oil supply apparatus for an internal combustion engine comprising a supply passage, a hydraulic control mechanism that controls the hydraulic pressure of the supply passage, and a diagnostic unit that performs an abnormality diagnosis on the hydraulic control mechanism,
The diagnostic oil supply device for an internal combustion engine, wherein the diagnosis unit prohibits execution of an abnormality diagnosis for the hydraulic control mechanism when it is determined that air suction of the oil pump occurs. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 4,
When the diagnosis means determines that the oil pressure in the supply passage is smaller than the oil pressure determination value and that the air suction of the oil pump occurs, the oil pressure in the supply passage is caused by the air suction. A lubricating oil supply device for an internal combustion engine, characterized in that it is determined that the position is below the range. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 5,
The diagnosis unit determines that air suction of the oil pump is occurring based on an oil level of the storage unit being lower than a level determination value. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 6,
The diagnostic means determines that an abnormality has occurred in the hydraulic control mechanism when determining that the hydraulic pressure in the supply passage is smaller than a hydraulic pressure determination value and that air suction of the oil pump has not occurred. A lubricating oil supply device for an internal combustion engine. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 7,
The diagnostic means performs a fail-safe operation of the internal combustion engine when it is determined that the hydraulic pressure in the supply passage is smaller than a hydraulic pressure determination value and that the air suction of the oil pump has not occurred. Lubricating oil supply device. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 8,
The hydraulic control mechanism switches a pressure for relief of the lubricating oil in the supply passage between a first relief pressure on the low pressure side and a second relief pressure on the high pressure side,
When the diagnosis means determines that the oil pressure in the supply passage is smaller than the oil pressure determination value and that the air suction of the oil pump does not occur, the hydraulic pressure control mechanism changes the relief pressure from the first relief pressure to the second relief pressure. A lubricating oil supply device for an internal combustion engine, characterized in that an abnormality that makes it impossible to switch to pressure has occurred. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 9,
The hydraulic control mechanism includes a hydraulic control valve that relieves the lubricating oil to the upstream side of the oil pump based on the pressure of the lubricating oil discharged from the oil pump exceeding a predetermined relief pressure. The predetermined relief pressure is switched between a first relief pressure and a second relief pressure by a 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 when the operation state is maintained in the second operation state. The lubricating oil supply apparatus for an internal combustion engine, wherein the predetermined relief pressure is set to a second relief pressure. The lubricating oil supply device for an internal combustion engine according to claim 10,
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 a first relief pressure and a second relief pressure by manipulating the position of the movable body. . The lubricating oil supply device for an internal combustion engine according to claim 11,
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 has the predetermined relief pressure set to the first relief pressure based on the movable body being maintained at the first movable position, and the movable body is maintained at the second movable position. The predetermined relief pressure is set to the second relief pressure based on
When the diagnosis means determines that the oil pressure of the supply passage is smaller than the oil pressure determination value and that air suction of the oil pump has not occurred, at least one abnormality of the valve body, the movable body, and the switching valve is detected. It is determined that the oil pressure in the supply passage is below the oil pressure determination value due to the above.

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