JP2010150987A - 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 suppressing unnecessary consumption of lubricating oil due to injection of the lubricating oil from an oil jet. <P>SOLUTION: The lubricating oil supply device 50 of this engine 10 controls pressure of a supply passage 52 for supplying the lubricating oil to the oil jet 56 by a hydraulic control mechanism 60. The lubricating oil supply device includes the hydraulic control mechanism 60 that releases the lubricating oil to an upstream side of an oil pump 53 when a supply pressure supplied from the supply passage 52 to the control mechanism 60 exceeds a predetermined relief pressure PX. The relief pressure PX is switched between a first relief pressure P1 and a second relief pressure P2 which is larger than the first relief pressure P1 and the relief pressure PX is switched from the second relief pressure P2 to the first relief pressure P1 on the basis of execution of fuel cut. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention controls the pressure for supplying lubricating oil to the oil jet by a hydraulic control mechanism, and when the pressure of the lubricating oil supplied to the control mechanism from the supply passage exceeds a predetermined relief pressure, The present invention relates to a lubricating oil supply device for an internal combustion engine provided with a relief.

In addition to the one described in Patent Document 1, conventional lubricating oil supply devices for internal combustion engines are provided with an oil jet that injects lubricating oil to cool the piston. In general, the oil jet is configured such that when the hydraulic pressure is equal to or higher than a predetermined value, the nozzle is opened to inject lubricating oil.
JP 2007-40148 A

  However, the conventional lubricating oil supply device avoids unnecessary consumption of the lubricating oil because the lubricating oil is injected from the oil jet in the same way as during normal operation even during fuel cut where the piston cooling requirement is small. It is not possible. In addition, since the in-cylinder negative pressure becomes relatively large at the time of fuel cut, the lubricating oil injected from the oil jet and around the piston is sucked into the combustion chamber through the gap between the cylinder wall surface and the piston. Further consumption will occur.

  The present invention has been made in view of such circumstances, and an object of the present invention is an internal combustion engine capable of suppressing unnecessary consumption of the lubricating oil due to the injection of the lubricating oil from the oil jet. It is to provide a lubricating oil supply device.

In the following, means for achieving the above object and its effects are described.
(1) The invention according to claim 1 controls the pressure of the supply passage for supplying lubricating oil to the oil jet by a hydraulic control mechanism, and the hydraulic control mechanism is connected to the control mechanism from the supply passage. In a lubricating oil supply apparatus for an internal combustion engine comprising a device that relieves the lubricating oil to a predetermined portion when the pressure of the supplied lubricating oil exceeds a predetermined relief pressure, the predetermined relief pressure is defined as the first relief pressure. And a control means for switching the relief pressure from the second relief pressure to the first relief pressure based on execution of fuel cut. It is a summary.

  According to the present invention, since the relief pressure of the hydraulic control mechanism is set to the first relief pressure on the low pressure side during the fuel cut, the relief pressure of the control mechanism is set to the second pressure on the high pressure side. The amount of lubricating oil injected from the oil jet is less than when the relief pressure is set. Accordingly, it is possible to suppress unnecessary consumption of the lubricating oil due to a large amount of the lubricating oil being injected from the oil jet during the fuel cut with a small piston cooling request. Further, unnecessary consumption of the lubricating oil due to the large amount of lubricating oil being sucked into the combustion chamber from the periphery of the piston can be suppressed.

  (2) According to a second aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the first aspect, the control means sets the predetermined relief pressure to the second level immediately before the fuel cut is performed. The gist is to switch from the second relief pressure to the first relief pressure based on the fact that the relief pressure is set to the first relief pressure.

  (3) According to a third aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the first or second aspect, the hydraulic control mechanism is configured to perform the predetermined operation based on the engine rotation speed being in a low rotation region. The gist is that the relief pressure is set to the first relief pressure, and the predetermined relief pressure is set to the second relief pressure based on the engine rotational speed being in a high rotation region.

  (4) The invention according to claim 4 is for controlling the pressure of the supply passage for supplying the lubricating oil to the oil jet by a hydraulic control mechanism, and as the hydraulic control mechanism, the supply passage is connected to the control mechanism. In the lubricating oil supply device for an internal combustion engine, which includes a device that relieves the lubricating oil to a predetermined portion when the pressure of the supplied lubricating oil exceeds a predetermined relief pressure, the relief is performed based on execution of fuel cut. The gist is to provide a control means for making the pressure smaller than the relief pressure immediately before the fuel cut is started.

  According to this invention, during the fuel cut, the relief pressure of the hydraulic control mechanism is set to be smaller than the relief pressure immediately before the fuel cut is started. The amount of lubricating oil injected from the oil jet is smaller than when the pressure is set higher than the relief pressure immediately before the start of cutting. Accordingly, it is possible to suppress unnecessary consumption of the lubricating oil due to a large amount of the lubricating oil being injected from the oil jet during the fuel cut with a small piston cooling request. Further, unnecessary consumption of the lubricating oil due to the large amount of lubricating oil being sucked into the combustion chamber from the periphery of the piston can be suppressed.

  (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 lubricating oil supply device lubricates from an oil pan to the oil jet. The hydraulic control mechanism includes the supply passage for supplying oil, and an oil pump provided in the middle of the supply passage for discharging the oil in the oil pan toward the oil jet. The gist is that the lubricating oil is relieved on the basis that the pressure of the lubricating oil discharged from the oil pump exceeds the predetermined relief pressure.

  (6) According to a sixth aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the fifth aspect, the hydraulic control mechanism connects the upstream side and the downstream side of the oil pump in the supply passage. A control passage, and a hydraulic control valve that is provided in the control passage and 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 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 with respect to the valve body, and a movable body that is provided between the valve body and the valve body and moves with respect to the valve body is configured. Yes, the valve The 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 communicates with the movable inlet, and is provided between the main body outlet and the oil chamber. A movable outlet that communicates with the valve body, and moves between a first movable position and a second movable position with respect to the valve body, and the first movable position. And the main body inlet and the movable inlet are kept in communication with each other and the main body outlet and the movable outlet are in communication with each other at any of the second movable positions. Is a small position relative to the valve body. In addition, the first valve body range that is closer to the movable inlet and the second valve body range that is further away from the movable inlet and the third valve body that is further away from the movable inlet. Any of the above-mentioned valve body range and a fourth valve body range that is further away from the movable inlet, and when in the first valve body range regardless of the position of the movable body, The flow between the movable inlet and the movable outlet is blocked to block the flow of lubricating oil from the main body inlet to the main body outlet, and when the movable body is in the first movable position, When the movable body is in the range of 2 valve bodies, 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 the movable body is the second valve body. Before when in the movable position When in the third valve body range, the flow between the movable inlet and the movable outlet is blocked to block the flow of lubricating oil from the main body inlet to the main body outlet, and the movable body is When in the second movable position and in the fourth valve body range, the movable inlet communicates with the movable outlet, and the switching mechanism operates the position of the movable body. Thus, the gist is that the predetermined relief pressure is switched between a first relief pressure and a second relief pressure higher than the first relief pressure.

  (7) The invention according to claim 7 is the lubricating oil supply apparatus for an internal combustion engine according to claim 6, wherein the switching mechanism is configured such that the oil is provided between the valve body and the movable body in the hydraulic control valve. A switching chamber provided separately from the chamber, a movable passage branched from the control passage and connected to the switching chamber, and supply of lubricating oil from the control passage to the switching chamber via the movable passage The movable body is set to the first movable position based on the supply of lubricating oil to the switching chamber via the movable passage. The hydraulic control valve is set to the second movable position based on the supply of lubricating oil to the switching chamber being cut off, and the hydraulic control valve is configured such that the movable body is moved to the first movable position. The predetermined relief pressure based on what is maintained The predetermined relief pressure is set to the second relief pressure based on the fact that the movable body is maintained at the second movable position. A request to set the predetermined relief pressure to the second relief pressure by maintaining the switching valve in an open state based on a request to set the predetermined relief pressure to the first relief pressure. The gist is to maintain the switching valve in a closed state based on the fact that

  (8) According to an eighth aspect of the present invention, in the lubricating oil supply device for an internal combustion engine according to the seventh aspect, the control means opens the switching valve based on the fact that fuel cut is being performed. The main point is to maintain it.

1 to 6, an embodiment in which the lubricating oil supply device for an internal combustion engine according to the present invention is embodied as an electronically controlled lubricating oil supply device for a vehicle will be described.
As shown in FIG. 1, the engine 10 includes an engine main body 20 that generates power through combustion of an air-fuel mixture, a lubricating oil supply device 50 that supplies lubricating oil to each lubricating portion of the engine 10, and these devices. And an electronic control unit 70 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 40 via the injector 31 and air supplied to the combustion chamber 40 through the intake device. The cylinder block 21 is provided with a plurality of cylinders 21 </ b> A that each form a combustion chamber 40. A piston 23 is provided in the cylinder 21A. 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 51 for storing lubricating oil is provided at the lower portion of the cylinder block 21. The lubricating oil in the oil pan 51 is supplied to each lubricating part of the engine body 20 through an oil pump 53 driven by the crankshaft 25.

  An oil jet 56 that injects lubricating oil toward the inner surface of the piston 23 is provided below the cylinder 21 </ b> A in the cylinder block 21. Lubricating oil discharged from the oil pump 53 is supplied to the oil jet 56.

  The cylinder head 22 is provided with an intake valve 27 for opening and closing the intake port of the cylinder 21A. An intake camshaft 26 is provided above the intake valve 27 to push it down by an intake cam 26a. The intake camshaft 26 is drivingly connected to the crankshaft 25 via a timing chain.

  The cylinder head 22 is provided with an exhaust valve 29 that opens and closes an exhaust port of the cylinder 21A. An exhaust camshaft 28 is provided above the exhaust valve 29 to push it down by an exhaust cam 28a. The exhaust camshaft 28 is drivingly connected to the crankshaft 25 via a timing chain.

  In the cylinder head 22, a cam shower 58 for injecting lubricating oil to these shafts is provided above the intake camshaft 26 and the exhaust camshaft 28. The cam shower 58 is supplied with lubricating oil discharged from the oil pump 53.

  The lubricating oil supply device 50 supplies the lubricating oil in the oil pan 51 to each lubricating portion of the engine body 20 through the supply passage 52. In the middle of the supply passage 52, an oil pump 53 is provided for pumping the lubricating oil from the oil pan 51 and discharging it. An oil strainer 54 that filters relatively large foreign substances contained in the lubricating oil in the oil pan 51 is provided at the inlet of the supply passage 52. In the supply passage 52, an oil filter 55 for filtering minute foreign matters contained in the lubricating oil is provided in the vicinity of the downstream side of the oil pump 53.

  The supply passage 52 includes a main supply passage 52A through which lubricating oil flows from the oil pan 51 to a predetermined portion of the engine main body 20, and an oil jet passage 52B and a cam shower passage 52C branched from the main supply passage 52A. Is provided. The oil jet passage 52 </ b> B supplies lubricating oil in the main supply passage 52 </ b> A discharged by the oil pump 53 to the oil jet 56. The cam shower passage 52 </ b> C supplies the lubricating oil in the main supply passage 52 </ b> A discharged by the oil pump 53 to the cam shower 58. An oil jet valve 57 for opening and closing the passage 52B is provided in the middle of the oil jet passage 52B. The oil jet valve 57 is opened when the piston 23 is in an engine operating state in which the temperature of the piston 23 is high, whereby the lubricating oil is injected from the oil jet 56. On the other hand, the valve is closed when the temperature of the piston 23 is low, and the injection of lubricating oil from the oil jet 56 is stopped.

  In the lubricating oil supply device 50, the lubricating oil discharged from the oil pump 53 in the supply passage 52 is returned to the upstream side of the pump 53, whereby the pressure of the lubricating oil in the supply passage 52 (hereinafter referred to as “supply hydraulic pressure P”). ) Is provided.

  The hydraulic control mechanism 60 is provided with a relief passage 63 that connects the upstream side and the downstream side of the oil pump 53 in the main supply passage 52A. The relief passage 63 is opened when the pressure of the lubricating oil discharged from the oil pump 53 becomes equal to or higher than a predetermined relief pressure (hereinafter referred to as “relief pressure PX”), and from the downstream side of the oil pump 53. A relief valve 61 for returning the lubricating oil is provided on the upstream side. The relief passage 63 is connected to a switching valve passage 64 that supplies lubricating oil on the inlet side of the relief valve 61 to the switching chamber 67 d of the valve 61. The switching valve passage 64 is provided with a switching valve 62 for switching the open / closed state of the passage 64.

  The switching valve 62 switches the relief pressure PX of the relief valve 61 by controlling the supply mode of the lubricating oil to the switching chamber 67d. That is, when lubricating oil is supplied to the switching chamber 67d when the switching valve 62 is in the open state, the relief pressure PX of the relief valve 61 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 67d is shut off due to the switching valve 62 being in the closed state, the relief pressure PX of the relief valve 61 is higher than the first relief pressure P1. The second relief pressure (hereinafter referred to as “second relief pressure P2”).

  When the relief pressure PX is set to the first relief pressure P1, the relief valve 61 opens based on the supply hydraulic pressure P exceeding the first relief pressure P1, and thereby the lubrication discharged from the oil pump 53 is performed. The oil is relieved upstream of the pump 53. Further, when the relief pressure PX is set to the second relief pressure P2, the valve is opened based on the supply hydraulic pressure P exceeding the second relief pressure P2, whereby the lubricating oil discharged from the oil pump 53 can be Relief to the upstream side of the pump 53.

  The lubricating oil supply device 50 includes an oil pan 51, a supply passage 52, an oil pump 53, an oil strainer 54, an oil filter 55, an oil jet 56, an oil jet valve 57, a cam shower 58, and a hydraulic control mechanism 60. Has been. The switching mechanism includes a switching chamber 67d, a switching valve passage 64, and a switching valve 62.

  The electronic control unit 70 grasps the engine operation state, the vehicle running state, and the driver's request based on signals from various sensors including an accelerator position sensor 71, a throttle position sensor 72, a crank position sensor 73, and an air flow meter 74. Then, for example, the following control is performed. That is, control such as throttle control for adjusting the intake air flow rate, injection control for adjusting the fuel injection amount by the injector 31, and hydraulic control for controlling the hydraulic pressure supplied to each lubrication part of the engine 10 is performed.

  The accelerator position sensor 71 outputs a signal corresponding to the depression amount of the accelerator pedal of the vehicle. The throttle position sensor 72 outputs a signal corresponding to the opening of the throttle valve. The crank position sensor 73 outputs a signal corresponding to the rotational speed of the crankshaft (hereinafter referred to as “engine rotational speed NE”). The air flow meter 74 outputs a signal corresponding to the mass flow rate of the intake air flowing through the intake passage.

  Here, in the hydraulic pressure control, the switching valve 62 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 the respective lubrication parts of the engine body 20. Specifically, when the engine speed NE is in the low rotation range or the middle rotation range, the relief pressure PX is set to the first relief pressure P1 through the control of the switching valve 62. On the other hand, when the engine rotation speed NE is in the high rotation region, the relief pressure PX is set to the second relief pressure P2 through the control of the switching valve 62.

A specific configuration of the hydraulic control mechanism 60 will be described in detail with reference to FIG. In addition, the part enclosed with the broken line in the figure shows the relief valve 61.
The hydraulic control mechanism 60 includes a relief passage 63 that connects the upstream side and the downstream side of the oil pump 53 in the supply passage 52, and the pressure of the lubricating oil that is provided in the relief passage 63 and discharged from the oil pump 53 is a relief pressure. A relief valve 61 that relieves lubricating oil to the upstream side of the oil pump 53 based on exceeding PX, and a switching valve 62 that switches the relief pressure PX by operating the relief valve 61 are configured.

  The relief valve 61 is provided with a cylindrical housing 65. The housing 65 is formed with an oil chamber 66 for retaining lubricating oil. The oil chamber 66 is provided with a cylindrical sleeve 67. The sleeve 67 moves in the axial direction (hereinafter referred to as “axial direction X”) with respect to the housing 65. The oil chamber 66 inside the sleeve 67 is provided with a columnar piston 68. The piston 68 moves in the axial direction X with respect to the housing 65 and the sleeve 67.

  The housing 65 has a housing inlet 65 b that communicates the relief passage 63 downstream of the oil pump 53 and the oil chamber 66, and a housing outlet 65 c that communicates the relief passage 63 upstream of the oil pump 53 and the oil chamber 66. And are formed. Regarding both ends of the housing 65 in the axial direction X, one of them is closed by the bottom wall 65a and the other is opened.

  The sleeve 67 includes a sleeve inlet 67b that is located between the housing inlet 65b and the oil chamber 66 and communicates with the sleeve 67, and a sleeve outlet 67c that is located between the housing outlet 65c and the oil chamber 66 and communicates with them. Is formed. Regarding both ends in the axial direction X of the sleeve 67, one of them is closed by the bottom wall 67a and the other is opened.

  The sleeve 67 is provided in the housing 65 in such a manner that the opening in the axial direction X opens in the same direction as the opening of the housing 65 and the outer peripheral surface of the sleeve 67 contacts the inner peripheral surface of the housing 65. Thereby, when the sleeve 67 moves to the bottom wall 65a side with respect to the housing 65 as much as possible, the bottom wall 67a of the sleeve 67 and the bottom wall 65a of the housing 65 come into contact with each other.

  The openings of the housing 65 and the sleeve 67 are closed by a closing body 69 formed as a separate body. The closing body 69 is fixed to the housing 65 and the sleeve 67 in a state where the main body 69a is inserted into the opening of the sleeve 67 and the flange 69b is abutted against the end surface 65e of the housing 65. .

  The sleeve 67 has a position where the end surface 67e abuts against the flange portion 69b of the closing body 69 from a position where the bottom wall 67a abuts against the bottom wall 65a of the housing 65 (hereinafter “first movable position X1”). X2 ") is allowed to move relative to the housing 65. Further, a force is applied from the first movable position X1 to the second movable position X2 by a separate spring. The state in which the housing inlet 65b and the sleeve inlet 67b communicate with each other and the state in which the housing outlet 65c and the sleeve outlet 67c communicate with each other are maintained even when both the first movable position X1 and the second movable position X2 are present.

  When the sleeve 67 is in the first movable position X1, a switching chamber 67d for retaining lubricating oil is formed between the end surface 67e of the sleeve 67 and the flange portion 69b of the closing body 69. In the housing 65, a switching port 65d that connects the switching valve passage 64 and the switching chamber 67d is provided at a location corresponding to the switching chamber 67d.

  When the sleeve 67 is in the second movable position X2, the end face 67e of the sleeve 67 and the flange portion 69b of the closing body 69 come into contact with each other, so that the switching chamber 67d is not formed between them.

  The piston 68 is located at least in a range close to the sleeve inlet 67b (hereinafter referred to as “first opening / closing range Y1”) as a position relative to the housing 65, and in a range further away from the sleeve inlet 67b (hereinafter referred to as “ 2nd opening / closing range Y2 "), a range further away from the sleeve inlet 67b (hereinafter referred to as" third opening / closing range Y3 "), and a range further away from the sleeve inlet 67b (hereinafter referred to as" third opening / closing range Y3 "). , “Fourth open / close range Y4”).

  Here, the first opening / closing range Y1 is cut off between the sleeve inlet 67b and the sleeve outlet 67c, that is, between the sleeve outlet 67c and the oil chamber 66 regardless of the position of the sleeve 67, and from the housing inlet 65b to the housing outlet 65c. The range of the position of the piston 68 which interrupts | blocks the flow of this lubricating oil is shown.

  Further, the second opening / closing range Y2 communicates between the sleeve inlet 67b and the sleeve outlet 67c, that is, between the sleeve outlet 67c and the oil chamber 66 when the sleeve 67 is in the first movable position X1, and from the housing inlet 65b. The range of the position of the piston 68 which permits the flow of the lubricating oil to the housing outlet 65c is shown. Since the first opening / closing range Y1 and the second opening / closing range Y2 are continuous ranges, the position of the piston 68 that is farthest from the bottom wall 67a in the first opening / closing range Y1 and the bottom wall 67a in the second opening / closing range Y2. The position of the piston 68 closest to is substantially the same.

  Further, the third opening / closing range Y3 is configured such that when the sleeve 67 is in the second movable position X2, the space between the sleeve inlet 67b and the sleeve outlet 67c, that is, between the sleeve outlet 67c and the oil chamber 66, is blocked from the housing inlet 65b. The range of the position of the piston 68 which interrupts | blocks the flow of the lubricating oil to the housing exit 65c is shown. Since the second opening / closing range Y2 and the third opening / closing range Y3 are continuous ranges, the position of the piston 68 farthest from the bottom wall 67a in the second opening / closing range Y2 and the bottom wall 67a in the third opening / closing range Y3. The position of the piston 68 closest to is substantially the same.

  The fourth opening / closing range Y4 communicates between the sleeve inlet 67b and the sleeve outlet 67c, that is, between the sleeve outlet 67c and the oil chamber 66 when the sleeve 67 is at the second movable position X2, and from the housing inlet 65b. The range of the position of the piston 68 which permits the flow of the lubricating oil to the housing outlet 65c is shown. Since the third opening / closing range Y3 and the fourth opening / closing range Y4 are continuous ranges, the position of the piston 68 farthest from the bottom wall 67a in the third opening / closing range Y3 and the bottom wall 67a in the fourth opening / closing range Y4. The position of the piston 68 closest to is substantially the same.

With reference to FIGS. 3 and 4, an operation mode of the hydraulic control mechanism 60 will be described.
FIG. 3 shows a change in the operation mode of the hydraulic control mechanism 60 as the supply hydraulic pressure P increases when the switching valve 62 is in the open state, that is, when the sleeve 67 is at the first movable position X1.

  As shown in FIG. 3A, when the supply hydraulic pressure P is less than the first relief pressure P1, the piston 68 is held close to the bottom wall 67a of the sleeve 67 due to the relationship between the supply hydraulic pressure P and the spring 66d. Is done. That is, the position of the piston 68 with respect to the housing 65 is held within the first opening / closing range Y1.

  Thereby, the space between the sleeve inlet 67b and the sleeve outlet 67c is blocked through the piston 68, and the flow of the lubricating oil from the housing inlet 65b to the housing outlet 65c is also blocked. For this reason, the lubricating oil supplied to the relief valve 61 is not relieved, and the supply hydraulic pressure P tends to increase rapidly toward the first relief pressure P1. In addition, the piston 68 moves in a direction away from the bottom wall 67a 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 68 moves away from the bottom wall 67a beyond the first opening / closing range Y1 due to the relationship between the supply hydraulic pressure P and the spring 66d. It is held at a distance. That is, the position of the piston 68 with respect to the housing 65 is held within the second opening / closing range Y2.

  Thereby, the sleeve inlet 67b and the sleeve outlet 67c communicate with each other, and the flow of lubricating oil from the housing inlet 65b to the housing outlet 65c is allowed. For this reason, the lubricating oil supplied to the relief valve 61 is relieved upstream of the oil pump 53. At this time, although the supply hydraulic pressure P tends to increase with an increase in the discharge amount of the oil pump 53, the degree thereof becomes gentler than when the supply hydraulic pressure P is less than the first relief pressure P1. In addition, the piston 68 moves further away from the bottom wall 67a due to the increase in the supply hydraulic pressure P. However, as long as the relief pressure PX is set to the first relief pressure P1, the supply hydraulic pressure P is the same as described above. Shows a gradual upward trend.

FIG. 4 shows a change in the operation mode of the hydraulic control mechanism 60 as the supply hydraulic pressure P increases when the switching valve 62 is in the closed state, that is, when the sleeve 67 is at the second movable position X2.
As shown in FIG. 4A, when the supply hydraulic pressure P is between the first relief pressure P1 and the second relief pressure P2, the piston 68 is moved to the second position due to the relationship between the supply hydraulic pressure P and the spring 66d. It is held at a position farther from the bottom wall 67a than the opening / closing range Y2. That is, the position of the piston 68 with respect to the housing 65 is held in the third opening / closing range Y3.

  Here, the position of the piston 68 farthest from the bottom wall 67a in the second opening / closing range Y2 and the position of the piston 68 closest to the bottom wall 67a in the third opening / closing range Y3 are substantially the same position, When the sleeve 67 is in the second movable position X2, it is located farther from the housing inlet 65b than when it is in the first movable position X1. Therefore, immediately after the sleeve 67 is switched from the first movable position X1 to the second movable position X2, when the piston 68 is at the position farthest from the bottom wall 67a in the second opening / closing range Y2, the piston 68 is moved to the position of the piston 68. Even when there is no substantial change, the sleeve inlet 67b is closed by the piston 68, unlike when the sleeve 67 is in the first movable position X1 (FIG. 3B). As long as the piston 68 is within the third opening / closing range Y3, this state is maintained.

  Thereby, the space between the sleeve inlet 67b and the sleeve outlet 67c is blocked through the piston 68, and the flow of the lubricating oil from the housing inlet 65b to the housing outlet 65c is also blocked. For this reason, the lubricating oil supplied to the relief valve 61 is not relieved, and the supply hydraulic pressure P tends to increase rapidly toward the second relief pressure P2. In addition, the piston 68 moves in a direction away from the bottom wall 67a due to the increase in the supply hydraulic pressure P, but is held 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 68 is further away from the bottom wall 67a than the third opening / closing range Y3 due to the relationship between the supply hydraulic pressure P and the spring 66d. Held in place. That is, the position of the piston 68 with respect to the housing 65 is held within the fourth opening / closing range Y4.

  Thereby, the sleeve inlet 67b and the sleeve outlet 67c communicate with each other, and the flow of lubricating oil from the housing inlet 65b to the housing outlet 65c is allowed. For this reason, the lubricating oil supplied to the relief valve 61 is relieved upstream of the oil pump 53. At this time, the supply hydraulic pressure P tends to increase with the increase in the discharge amount of the oil pump 53, but 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 67 is in the second movable position X2, it is formed in the housing 65 separately from the oil chamber 66 and the switching chamber 67d. Lubricating oil is supplied to the auxiliary chamber. That is, the switching valve 62 is opened and the lubricating oil in the relief passage 63 is supplied to the auxiliary chamber via the switching valve passage 64. Accordingly, the sleeve 67 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 67 is held at the first movable position X1, and the supply hydraulic pressure P is less than the first relief pressure P1, so that the piston 68 is It is held in the first opening / closing range Y1. That is, the relief valve 61 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 higher than the first relief pressure P1, and the piston 68 is pushed down to the second opening / closing range Y2. As a result, the relief valve 61 is opened and a part of the lubricating oil discharged from the oil pump 53 is relieved to the upstream side of the pump 53.

  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 67 is held at the first movable position X1, and the supply hydraulic pressure P is the first relief pressure P1. Due to the above, the piston 68 is held in the second opening / closing range Y2. That is, the relief valve 61 is in a state where the relief pressure PX is set to the first relief pressure P1 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 61 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 67 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 61 is switched from the first relief pressure P1 to the second relief pressure P2. Thereby, since the sleeve outlet 67c is closed by the piston 68, the relief valve 61 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 67 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 68 is held in the third opening / closing range Y3. That is, the relief valve 61 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 68 is pushed down to the fourth opening / closing range Y4. As a result, the relief valve 61 is opened and a part of the lubricating oil discharged from the oil pump 53 is relieved to the upstream side of the pump 53.

  When the engine rotational speed NE is in a region greater than the third rotational speed NE3, the sleeve 67 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, thereby causing the piston 68 to move. It is held in the fourth opening / closing range Y4. That is, the relief valve 61 is in a state where the relief pressure PX is set to the second relief pressure P2 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 61 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

  By the way, when the supply hydraulic pressure P is switched by the relief valve 61 based on the engine rotational speed NE, when the fuel cut is started under the situation where the engine rotational speed NE is in the high rotational speed region. This leads to the following problem. That is, the relief pressure PX is maintained at the second relief pressure P2 on the high pressure side as long as the engine rotational speed NE is in the high rotation range, even though the cooling demand for the piston 23 is small due to the fuel cut. The injection amount of the oil jet 56 becomes relatively large accordingly. In addition, since the negative pressure in the combustion chamber 40 increases during a fuel cut, the lubricating oil injected from the oil jet 56 and around the piston 23 is sucked into the combustion chamber 40 through the gap between the wall surface of the cylinder 21A and the piston 23. It becomes like this. In other words, the lubricating oil exceeding the amount required to cool the piston 23 is injected from the oil jet 56, and a large amount of the injected lubricating oil is sucked into the combustion chamber 40, so that no lubricating oil is required. Will lead to unnecessary consumption.

  Therefore, in the present embodiment, the relief pressure PX of the relief valve 61 is set to the first relief pressure P1 in order to reduce the injection amount of the lubricating oil from the oil jet 56 at the time of fuel cut.

  With reference to FIG. 6, the content of the “supply hydraulic pressure control process” executed including the hydraulic control at the time of fuel cut will be described. This process is repeatedly executed at predetermined control intervals by the electronic control unit 70 during operation of the engine 10.

  In this process, first, in step S110, it is determined whether or not a fuel cut is being executed. When it is determined that the fuel cut is not being executed, it is determined in the next step S120 whether or not the engine speed NE is in the 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 73 is equal to or higher than a predetermined determination value.

  If it is determined in step S120 that the engine speed NE is not in the high rotation range, the relief pressure PX of the relief valve 61 is set to the first relief pressure P1 in the next step S130. That is, energization to the switching valve 62 is executed. On the other hand, when it is determined that the engine rotation speed NE is in the high rotation region, the relief pressure PX of the relief valve 61 is set to the second relief pressure P2 in the next step S140. That is, the energization to the switching valve 62 is stopped.

  If it is determined in step S110 that the fuel cut is being executed, the relief pressure PX of the relief valve 61 is switched to the first relief pressure P1 in step S130. That is, energization to the switching valve 62 is executed. As a result, the supply hydraulic pressure P is maintained at a lower level than when the second relief pressure P2 is set, so that the injection amount of the lubricating oil from the oil jet 56 is reduced, and as a result, from the periphery of the piston 23 to the combustion chamber 40 The amount of lubricating oil sucked into is also reduced. Further, when the relief pressure PX of the relief valve 61 is switched to the first relief pressure P1 based on the fact that the fuel cut is being executed, the relief pressure PX is also the first as long as the fuel cut is continuously executed. The relief pressure P1 is maintained. After the fuel cut is completed, the relief pressure PX is set based on whether the engine speed NE is in the high rotation region, the low rotation region, or the medium rotation region through the processing in steps S120 to S140 described above. Done.

According to the lubricating oil supply device for an internal combustion engine of the present embodiment, the following effects can be obtained.
(1) In the present embodiment, since the relief pressure PX of the hydraulic control mechanism 60 is set to the first relief pressure P1 on the low pressure side during execution of the fuel cut, the relief pressure PX of the control mechanism 60 is The amount of lubricating oil injected from the oil jet 56 is smaller than when the second relief pressure P2 on the high pressure side is set. Accordingly, it is possible to suppress unnecessary consumption of the lubricating oil due to the large amount of the lubricating oil being injected from the oil jet 56 during the fuel cut with a small piston cooling request. Further, unnecessary consumption of the lubricating oil due to the large amount of lubricating oil being sucked into the combustion chamber 40 from the periphery of the piston 23 can be suppressed.

  (2) In the present embodiment, during the fuel cut, the relief pressure PX of the hydraulic control mechanism 60 is set to be smaller than the relief pressure PX immediately before the fuel cut is started. The amount of lubricating oil injected from the oil jet 56 is smaller than when the relief pressure PX of 60 is set higher than the relief pressure PX immediately before fuel cut is started. Accordingly, it is possible to suppress unnecessary consumption of the lubricating oil due to the large amount of the lubricating oil being injected from the oil jet 56 during the fuel cut with a small piston cooling request. Further, unnecessary consumption of the lubricating oil due to the large amount of lubricating oil being sucked into the combustion chamber 40 from the periphery of the piston 23 can be suppressed.

(Other embodiments)
The embodiment of the present invention is not limited to the above-described embodiment, and can be modified as shown below, for example.

In the above-described embodiment, the switching valve 62 that opens when energized is employed, but a valve that opens when de-energized can be used instead.
In the above embodiment, an electromagnetic valve is employed as the switching valve 62, but a switching valve that is driven by hydraulic pressure, negative pressure, or the like may be employed instead.

  In the above embodiment, the position of the sleeve 67 relative to the housing 65 is operated based on the force applied to the sleeve 67 by the lubricating oil in the switching chamber 67d. However, the configuration for this operation is the same as in the above embodiment. However, the configuration is not limited to those exemplified above. For example, an electric actuator for the sleeve 67 can be provided, and the position of the sleeve 67 can be changed through control of the actuator.

In the above-described embodiment, the configuration in which the lubricating oil is supplied by the engine-driven oil pump 53 is employed, but an electric oil pump may be employed instead.
In the above embodiment, the hydraulic pressure control mechanism 60 that can switch the relief pressure PX to the two stages of the first relief pressure P1 and the second relief pressure P2 for each part of the engine 10 is provided. As long as the relief pressure P1 and the second relief pressure P2 can be selected, the switching stage of the supply hydraulic pressure P is not limited to two stages. For example, as the hydraulic control mechanism 60, a mechanism that switches the relief pressure PX to three or more stages, or a mechanism that continuously changes the relief pressure PX can be employed. In this case, based on the determination that the fuel cut is being performed, the supply hydraulic pressure P is made smaller than that immediately before the start of the fuel cut, so that the operation effect similar to the operation effect of the above embodiment is achieved. I can play.

  In the above embodiment, as the hydraulic control mechanism 60, 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 67 with respect to the housing 65 is adopted, but the relief pressure PX The configuration for switching between is not limited to this. For example, the relief pressure can be switched by providing two pressure adjusting valves with different control pressures in the hydraulic control mechanism 60 and selecting one of them.

  After all, the present invention can be applied to any supply device as long as it is a lubricant supply device that controls the pressure of the lubricant supplied to the oil jet by setting the relief pressure. The configuration is not limited to the configuration illustrated in the above embodiment. And, as long as it is an embodiment of the invention within a range that satisfies these conditions, the effects according to the above embodiment can be achieved in any case.

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

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

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

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Engine, 20 ... Engine main body, 21 ... Cylinder block, 21A ... Cylinder, 22 ... Cylinder head, 23 ... Piston, 24 ... Connecting rod, 25 ... Crankshaft, 26 ... Intake camshaft, 26a ... Intake cam, 27 ... Intake valve, 28 ... exhaust camshaft, 28a ... exhaust cam, 29 ... exhaust valve, 31 ... injector, 40 ... combustion chamber, 50 ... lubricating oil supply device, 51 ... oil pan, 52 ... supply passage, 52A ... main supply passage 52B ... Oil jet passage, 52C ... Cam shower passage, 53 ... Oil pump, 54 ... Oil strainer, 55 ... Oil filter, 56 ... Oil jet, 57 ... Oil jet valve, 58 ... Cam shower, 60 ... Hydraulic pressure Control mechanism, 61 ... relief valve (hydraulic control valve), 62 ... switching bar (Switching valve), 63 ... relief passage (control passage), 64 ... switching valve passage (movable passage), 65 ... housing (valve body), 65a ... bottom wall, 65b ... housing inlet (body inlet), 65c ... Housing outlet (main body outlet), 65d ... switching port, 65e ... end face, 66 ... oil chamber, 66d ... spring, 67 ... sleeve (movable body), 67a ... bottom wall, 67b ... sleeve inlet (movable inlet), 67c ... sleeve Outlet (movable outlet), 67d ... switching chamber, 67e ... end face, 68 ... piston (valve), 69 ... closed body, 69a ... main body, 69b ... flange, 70 ... electronic control device, 71 ... accelerator position sensor, 72: Throttle position sensor, 73: Crank position sensor, 74: Air flow meter.

Claims (8)

The pressure of the supply passage for supplying the lubricating oil to the oil jet is controlled by a hydraulic control mechanism, and the pressure of the lubricating oil supplied from the supply passage to the control mechanism is a predetermined relief pressure as the hydraulic control mechanism. In a lubricating oil supply device for an internal combustion engine comprising a device that relieves the lubricating oil to a predetermined site when exceeding
The predetermined relief pressure is switched between a first relief pressure and a second relief pressure higher than the first relief pressure, and the relief pressure is changed from the second relief pressure based on the fact that a fuel cut is performed. A control means for switching to the first relief pressure is provided. A lubricating oil supply device for an internal combustion engine, comprising: The lubricating oil supply device for an internal combustion engine according to claim 1,
The control means changes the second relief pressure to the first relief pressure based on the fact that the predetermined relief pressure is set to the second relief pressure immediately before the fuel cut is executed. A lubricating oil supply device for an internal combustion engine, characterized in that The lubricating oil supply device for an internal combustion engine according to claim 1 or 2,
The hydraulic control mechanism sets the predetermined relief pressure to the first relief pressure based on the engine rotational speed being in the low rotational range, and sets the predetermined relief pressure based on the engine rotational speed being in the high rotational range. A relief oil supply device for an internal combustion engine, wherein the relief pressure is set to the second relief pressure. The pressure of the supply passage for supplying the lubricating oil to the oil jet is controlled by a hydraulic control mechanism, and the pressure of the lubricating oil supplied from the supply passage to the control mechanism is a predetermined relief pressure as the hydraulic control mechanism. In a lubricating oil supply device for an internal combustion engine comprising a device that relieves the lubricating oil to a predetermined site when exceeding
A lubricating oil supply device for an internal combustion engine, comprising: control means for making the relief pressure smaller than the relief pressure immediately before the fuel cut is started based on execution of fuel cut. In the lubricating oil supply device for an internal combustion engine according to any one of claims 1 to 4,
The lubricating oil supply device includes an oil supply passage that supplies lubricating oil from an oil pan to the oil jet, and an oil that is provided in the middle of the supply passage and discharges the lubricating oil from the oil pan toward the oil jet. It is configured including a pump,
The lubricating oil supply device for an internal combustion engine, wherein the hydraulic control mechanism relieves the lubricating oil based on the pressure of the lubricating oil discharged from the oil pump exceeding the predetermined relief pressure. The lubricating oil supply device for an internal combustion engine according to claim 5,
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. A 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. Yes,
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 switching mechanism is configured to switch the predetermined relief pressure between a first relief pressure and a second relief pressure higher than the predetermined relief pressure by operating a position of the movable body. Engine lubricant supply device. The lubricating oil supply device for an internal combustion engine according to claim 6,
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,
In the hydraulic control valve, the predetermined relief pressure is set to the first relief pressure based on the movable body being maintained at the first movable position, and the movable body is moved to the second movable position. The predetermined relief pressure is set to the second relief pressure based on being maintained at
The control means maintains the switching valve in an open state based on a request to set the predetermined relief pressure to the first relief pressure, and the predetermined relief pressure is set to the second relief pressure. The lubricating oil supply device for an internal combustion engine, wherein the switching valve is maintained in a closed state based on a request to set to The lubricating oil supply device for an internal combustion engine according to claim 7,
The control means maintains the switching valve in an open state based on the fact that fuel cut is being executed. A lubricating oil supply apparatus for an internal combustion engine, wherein:

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