JP2018013070A - Oil supply device for engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil supply device capable of preventing the breakage of an oil filter in a simple configuration.SOLUTION: Between a pump chamber 365 of an oil pump 36 and an oil filter 37, a control oil path 90 is provided. The control oil path 90 is connected via an oil control valve 49 directly to a pressure chamber 369 of the oil pump 36. When the drive of the oil pump 36 is started with an engine 2 started, the oil control valve 49 is opened at a predetermined rate or higher to increase the amount of oil to flow into the control oil path 90 so that the high-viscosity oil does not flow into the oil filter 37 in large amount.SELECTED DRAWING: Figure 2

Description

  The technology disclosed herein relates to an engine oil supply apparatus.

  2. Description of the Related Art Conventionally, for example, oil is supplied through a hydraulic path to a hydraulic actuator of an engine such as a variable valve timing mechanism or a lubricating part such as an engine crankshaft by a variable displacement oil pump. By configuring the oil pump to have a variable capacity, it is possible to avoid unnecessary driving of the oil pump and improve fuel efficiency.

  For example, Patent Document 1 discloses a pump that can reduce power loss by bringing the pump discharge pressure close to the required hydraulic pressure.

  According to Patent Document 1, at high engine speed, the electromagnetic switching valve guides the hydraulic pressure to the second control oil chamber via the first and second solenoid control ports having an orifice effect, while the pilot valve is the first spool valve. In the initial position where the valve is urged by the first valve spring and moved to the maximum right direction, the communication state between the hydraulic pressure introduction port and the first pilot control port is cut off, and when the discharge pressure increases, the ports can be communicated with each other. The second pilot control port and the first drain port are communicated to control the hydraulic pressure in the first control oil chamber. Thus, when there is a request to maintain the desired discharge pressure, an excessive increase in the discharge pressure can be suppressed even if the pump speed increases.

JP 2013-130089 A

  By the way, especially when the engine is started in an environment with a low outside air temperature, the oil viscosity is high and the variable displacement oil pump is in the maximum volume state. There is a risk of damage.

  In order to solve such a problem, as shown in FIG. 11, a leak passage 900 is conventionally provided between the oil pump 36 and the oil filter 37 disposed downstream thereof, and the oil pan 6 is passed through the leak passage 900. However, it was necessary to attach a check valve 901 in the leak passage 900, and the structure was complicated.

  The technology disclosed herein has been made in view of the above points, and an object thereof is to provide an oil supply apparatus that can prevent the oil filter from being damaged with a simple configuration.

  In order to achieve the above object, in the present disclosure, a branch passage is provided between the working chamber of the oil pump and the oil filter, and the branch passage is directly connected to the control hydraulic chamber of the oil pump via the control valve. At the start of the oil pump when the engine is started, the control valve opening is set to a predetermined ratio or more to increase the oil flow rate to the branch passage so that a large amount of highly viscous oil does not flow into the oil filter.

  In other words, the engine oil supply device disclosed herein has a working chamber and a control hydraulic chamber, and the discharge capacity can be changed by changing the volume of the working chamber according to the pressure of the control hydraulic chamber. A variable capacity type oil pump, an oil supply passage communicating with the working chamber of the oil pump and connected to an oil supply section provided downstream of the oil pump, on the oil supply passage, An oil supply device for an engine comprising an oil filter disposed on the downstream side of the working chamber of the oil pump, wherein the oil supply path is a pump downstream oil connecting the working chamber of the oil pump and the oil filter. And a control oil passage branched from the pump downstream oil passage and connected to the control hydraulic chamber of the oil pump, provided on the control oil passage, and the opening degree is changed. A control valve configured to be able to change the oil flow rate of the control oil passage, a control unit that controls the opening of the control valve, and a start request detection for detecting a start request of the engine or the oil pump And when the start request detecting means detects the start request for the engine or the oil pump, the control unit is configured to supply oil to the control oil path before starting the oil pump drive. Control at the time of starting is performed so that the opening degree of the control valve is equal to or greater than a predetermined ratio so as to be able to flow.

  As described above, conventionally, a leak passage is provided between the oil pump working chamber and the oil filter, and excess oil leaks into the oil pan. However, in the conventional configuration, it is necessary to provide a check valve on the leak passage, which is a complicated configuration.

  According to the present technology, the control oil passage is provided between the oil pump working chamber and the oil filter, and the control oil passage is connected to the control oil pressure chamber of the oil pump via the control valve. Since it can be introduced directly into the control hydraulic chamber of the oil pump without leaking into the oil pan, the pump work can be reduced. In addition, the control unit makes the oil flow through the control oil passage by setting the opening of the control valve to a predetermined ratio or more at the start of driving of the oil pump at the time of engine start based on the engine or oil pump start request. By making it possible, it is possible to prevent the oil with high viscosity at the start of driving the oil pump from flowing into the oil filter and to prevent the oil filter from being damaged.

  The engine oil supply device disclosed herein has a working chamber and a control hydraulic chamber, and the discharge capacity can be changed by changing the volume of the working chamber according to the pressure of the control hydraulic chamber. A variable capacity type oil pump, an oil supply passage communicating with the working chamber of the oil pump and connected to an oil supply section provided downstream of the oil pump, on the oil supply passage, An oil supply device for an engine comprising an oil filter disposed on the downstream side of the working chamber of the oil pump, wherein the oil supply path is a pump downstream oil connecting the working chamber of the oil pump and the oil filter. And a control oil passage branched from the pump downstream oil passage and connected to the control hydraulic chamber of the oil pump, provided on the control oil passage, and the opening degree is changed. A control valve configured to be able to change the oil flow rate of the control oil passage, a control unit for controlling an opening degree of the control valve, and a start request detecting means for detecting a start request of the engine or the oil pump And a fluid temperature detection means for detecting a temperature of a fluid that is installed on the engine or a vehicle member on which the engine is mounted and that contacts the engine or the member, and the control unit includes the start request When the detection means detects the engine or the oil pump start request, the fluid temperature detection value detected by the fluid temperature detection means is read before the oil pump starts driving, and the fluid temperature detection means When the detected fluid temperature detection value is not more than a predetermined value, the opening of the control valve is not less than a predetermined ratio so that oil can flow through the control oil passage. And performing start control for.

  Here, in the present specification, “the engine or a member of the vehicle on which the engine is mounted” refers to an engine, components constituting the engine, members such as a structure, and a vehicle on which the engine is mounted. Components such as components, structures, etc., specifically, for example, exterior members such as oil supply passages, cylinder heads, water jackets, vehicle doors, engine exhaust gas passages, and the like. Further, the “fluid in contact with a member of the engine or the vehicle” is a fluid in contact with at least one of the inner surface and the outer surface of the member constituting the engine or the vehicle. It refers to fluids such as flowing oil, cooling water in a water jacket provided in the cylinder head, the atmosphere in contact with an exterior member such as a vehicle door, and exhaust gas flowing in the exhaust gas passage of the engine.

  When the temperature of the fluid in contact with the engine or vehicle member as described above is low, the viscosity of the oil is considered to be high. Therefore, according to the present technology, the temperature of the fluid in contact with the vehicle member is detected, and when the detected oil temperature is a low temperature below a predetermined value, the oil flow rate in the control oil passage is increased to a predetermined amount or more. Thus, the flow rate of the oil flowing into the oil filter can be reduced, and the oil filter can be prevented from being damaged.

The engine oil supply device disclosed herein has a working chamber and a control hydraulic chamber, and the discharge capacity can be changed by changing the volume of the working chamber according to the pressure of the control hydraulic chamber. A variable capacity type oil pump, an oil supply passage communicating with the working chamber of the oil pump and connected to an oil supply section provided downstream of the oil pump, on the oil supply passage, An oil supply device for an engine comprising an oil filter disposed on the downstream side of the working chamber of the oil pump, wherein the oil supply path is a pump downstream oil connecting the working chamber of the oil pump and the oil filter. And a control oil passage branched from the pump downstream oil passage and connected to the control hydraulic chamber of the oil pump, provided on the control oil passage, and the opening degree is changed. A control valve configured to be able to change the oil flow rate of the control oil passage, a control unit for controlling an opening degree of the control valve, and a start request detecting means for detecting a start request of the engine or the oil pump And fluid temperature detection means for detecting a temperature of a fluid that is installed on the engine or a vehicle member on which the engine is mounted and that contacts the engine or the member. Based on a storage unit that stores in advance a relationship between the viscosity of oil and a temperature, a fluid temperature detection value detected by the fluid temperature detection means, and a relationship between the fluid temperature and the viscosity stored in the storage unit, An estimation unit that estimates an oil viscosity and obtains an estimated viscosity value, and the control unit detects when the engine or the oil pump start request is detected by the start request detecting means. , Before start of driving the oil pump, reads the fluid temperature detection value detected by the fluid temperature detecting means,
When the estimated viscosity value estimated by the estimation unit based on the fluid temperature detection value and the relationship between the fluid temperature and the viscosity is greater than or equal to a predetermined value, the oil can flow through the control oil passage. The control at the time of starting which makes the opening degree of a control valve more than a predetermined ratio is performed.

  According to the present technology, the temperature of the fluid that contacts the vehicle member is detected, and based on the obtained fluid temperature detection value and the relationship between the fluid temperature and the viscosity of the oil stored in the storage unit in advance, When the viscosity is estimated and the estimated viscosity is higher than the specified value, the oil flow rate in the control oil passage is increased to a specified value or more to reduce the flow rate of oil flowing into the oil filter and damage the oil filter. Can be prevented.

  In a preferred aspect, the member is the pump downstream oil passage, the fluid is oil flowing through the pump downstream oil passage, and the fluid temperature detecting means detects the oil temperature upstream of the oil filter. Oil temperature detecting means configured as described above.

  According to the present technology, the oil temperature of the oil before flowing into the oil filter is detected, and when the detected oil temperature is a low temperature below a predetermined value, the oil flow rate in the control oil passage is increased to a predetermined amount or more. Thus, the flow rate of the oil flowing into the oil filter can be reduced, and the oil filter can be prevented from being damaged.

  Further, the oil temperature is detected, and based on the obtained oil temperature detection value and the relationship between the oil temperature and the viscosity of the oil stored in the storage unit in advance, the viscosity of the oil is estimated, and the estimated viscosity value is When the viscosity is higher than a predetermined value, the oil flow rate in the control oil passage is increased to a predetermined amount or more to reduce the oil flow rate flowing into the oil filter and prevent the oil filter from being damaged.

  In a preferred aspect, the member is a water cooling part of the engine, the fluid is cooling water of the water cooling part, and the fluid temperature detecting means detects a water temperature of the cooling water of the water cooling part. It is the water temperature detection means comprised in this.

  According to the present technology, for example, the temperature of cooling water in a water cooling part of an engine such as a water jacket of a cylinder head is detected, and when the detected water temperature is a low temperature below a predetermined value, the oil flow rate in the control oil passage is determined. By increasing the amount more than the fixed amount, the oil flow rate flowing into the oil filter can be reduced, and the oil filter can be prevented from being damaged.

  In addition, the water temperature is detected, the viscosity of the oil is estimated based on the obtained water temperature detection value and the relationship between the water temperature of the cooling water and the viscosity of the oil stored in advance in the storage unit. When the viscosity is higher than a predetermined value, the oil flow rate in the control oil passage is increased to a predetermined amount or more to reduce the oil flow rate flowing into the oil filter and prevent the oil filter from being damaged.

  In a preferred aspect, the member is an exterior member of the vehicle, the fluid is an atmosphere outside the vehicle, and the fluid temperature detection means is configured to detect an outside air temperature outside the vehicle. Outside air temperature detecting means.

  According to the present technology, for example, the temperature of the atmosphere in contact with an exterior member of a vehicle such as a vehicle door, that is, the outside air temperature is detected, and when the detected outside air temperature is a low temperature below a predetermined value, the oil in the control oil passage By increasing the flow rate to a predetermined amount or more, the oil flow rate flowing into the oil filter can be reduced, and the oil filter can be prevented from being damaged.

  Further, the outside air temperature is detected, and based on the obtained outside air temperature detection value and the relationship between the outside air temperature and the viscosity of the oil stored in the storage unit in advance, the viscosity of the oil is estimated. When the viscosity is higher than a predetermined value, the oil flow rate in the control oil passage is increased to a predetermined amount or more to reduce the oil flow rate flowing into the oil filter and prevent the oil filter from being damaged.

  In a preferred aspect, the control unit maximizes the opening of the control valve in the start-up control.

  At the time of starting the oil pump when starting the engine, the oil temperature of the normal oil is low and there is a possibility that it is in a highly viscous state. If a large amount of such low temperature and high viscosity oil flows into the oil filter, the oil filter may be damaged.

  According to the present technology, at the time of starting the oil pump at the start of the engine, the opening of the control valve is maximized and the oil flow rate in the control oil passage is maximized, so that the low temperature and high viscosity at the start of the oil pump driving The oil can be prevented from flowing into the oil filter, and the oil filter can be prevented from being damaged.

  In a preferred aspect, the oil pump includes a pump housing that houses the working chamber and has a discharge port for discharging oil from the working chamber, and the pump downstream oil passage is provided in the pump housing, A discharge passage that connects the working chamber and the discharge port; the control oil passage is branched from the discharge passage; and the control oil passage and the control valve are integrally formed with the pump housing. Yes.

  According to the present technology, the oil supply apparatus can be made compact by integrally forming the control oil passage and the control valve in the pump housing of the oil pump. Further, since the oil passage length of the control oil passage can be shortened compared to drilling the control oil passage in other engine parts, the pump work can be further reduced.

  In a preferred embodiment, the oil supply path has a hydraulic path that communicates with the downstream side of the oil filter and is connected to the oil supply unit, and is configured to detect a hydraulic pressure of the hydraulic path. The control unit further includes an oil discharge of the oil pump by adjusting an opening of the control valve so that a hydraulic pressure in the hydraulic path becomes a target hydraulic pressure when the control at the time of starting is not performed. When the start time control is performed, the start time control is performed when the oil pressure detection value detected by the oil pressure detection means becomes a predetermined value or more. To the feedback control.

  As shown in FIG. 11, in the conventional oil supply apparatus, the hydraulic pressure in the hydraulic path is feedback-controlled through the feedback control oil path 40 branched from the branch point 54b of the hydraulic path downstream from the oil filter and connected to the control valve. Was. According to the present technology, the control oil passage branched from the pump downstream oil passage can function as an oil passage for feedback control, and the control valve can also function as a hydraulic control valve for feedback control. Further reduction in the size of the oil pump can be realized. Further, as described above, since the oil has a high viscosity for a while from the start of driving the oil pump at the start of the engine, the oil filter may be damaged.

  According to the present technology, during the period from when the engine is started until the detected hydraulic pressure exceeds a predetermined value, the oil filter is prevented from being damaged by performing start-up control, and after the detected hydraulic pressure exceeds the predetermined value. Since the oil viscosity also decreases and the risk of oil filter breakage also decreases, the oil pressure in the hydraulic path can be controlled efficiently by changing to the normal feedback control of the oil pump. Further, when the start-time control is not performed, the normal feedback control can be performed from the start of driving the oil pump at the start of the engine, so that the hydraulic pressure in the hydraulic path can be controlled efficiently.

  In a preferred aspect, the oil supply passage has an oil pressure passage that communicates with a downstream side of the oil filter and is connected to the oil supply portion, and is configured to detect an engine speed of the engine. The control unit further includes a rotational speed detection means, and the control unit adjusts the opening of the control valve so that the hydraulic pressure in the hydraulic path becomes a target hydraulic pressure when the start time control is not performed. It is configured to perform feedback control for adjusting the oil discharge amount of the pump, and when performing the start-up control, the engine speed detection value detected by the engine speed detection means is greater than or equal to a predetermined speed. When this happens, the control at the start time is switched to the feedback control.

  According to the present technology, the start-up control is performed until the engine speed reaches the predetermined engine speed, thereby preventing the oil filter from being damaged, and after the engine speed reaches the predetermined engine speed, By changing to feedback control of the oil pump, the hydraulic pressure of the hydraulic path can be controlled efficiently. Further, when the start-time control is not performed, the normal feedback control can be performed from the start of driving the oil pump at the start of the engine, so that the hydraulic pressure in the hydraulic path can be controlled efficiently.

  As described above, according to the present technology, the control oil passage is provided between the working chamber of the oil pump and the oil filter, and the control oil passage is connected to the control hydraulic chamber of the oil pump via the control valve. As a result, surplus oil can be introduced directly into the control hydraulic chamber of the oil pump without leaking to the oil pan, so that pump work can be reduced. In addition, the control unit makes the oil flow through the control oil passage by setting the opening of the control valve to a predetermined ratio or more at the start of driving of the oil pump at the time of engine start based on the engine or oil pump start request. By making it possible, it is possible to prevent the oil with high viscosity at the start of driving the oil pump from flowing into the oil filter and to prevent the oil filter from being damaged.

FIG. 1 is a cross-sectional view illustrating a schematic configuration of a multi-cylinder engine to which an oil supply apparatus according to a first embodiment is applied. FIG. 2 is a diagram showing a schematic configuration of the hydraulic system. FIG. 3 is a schematic cross-sectional perspective view of the variable capacity oil pump with the cover member removed. 4 is a schematic front view of the variable capacity oil pump of FIG. 5 is a cross-sectional view taken along line AA in FIG. 6 is a cross-sectional view taken along line BB in FIG. 7 is a cross-sectional view taken along the line CC of FIG. FIG. 8 is a cross-sectional view schematically showing the internal structure of the oil control valve in FIG. FIG. 9 is a flowchart for explaining a control flow of the hydraulic system according to the first embodiment. FIG. 10 is a graph showing temporal changes in the oil pressure of the oil supply passage and the engine speed of the hydraulic system according to the first embodiment and the conventional hydraulic system. FIG. 11 is a flowchart for explaining a control flow of the hydraulic system according to the second embodiment. FIG. 12 is a flowchart for explaining a control flow of the hydraulic system according to the fifth embodiment. FIG. 13 is a diagram illustrating a schematic configuration of a hydraulic system including a conventional oil supply device.

  Hereinafter, embodiments of the present technology will be described in detail with reference to the drawings. The following description of the preferred embodiments is merely exemplary in nature and is in no way intended to limit the present technology, its application, or its use.

(First embodiment)
<About hydraulic system>
[Engine configuration]
FIG. 1 shows a multi-cylinder engine 2 (hereinafter simply referred to as an engine 2) to which an oil supply apparatus according to this embodiment is applied. The engine 2 is an in-line four-cylinder gasoline engine in which first to fourth cylinders are sequentially arranged in series in a direction perpendicular to the paper surface of FIG. 1 and is mounted on a vehicle such as a four-wheeled vehicle. In the engine 2, a cam cap 3, a cylinder head 4, a cylinder block 5, a crankcase (not shown), and an oil pan 6 (see FIG. 2) are connected to each other in the four cylinder bores 7 formed in the cylinder block 5. Are connected to each other by a connecting rod 10, and a combustion chamber 11 is connected by a cylinder bore 7, a piston 8, and a cylinder head 4 of the cylinder block 5. Is formed for each cylinder.

  The cylinder head 4 is provided with an intake port 12 and an exhaust port 13 that open to the combustion chamber 11, and an intake valve 14 and an exhaust valve 15 that open and close the intake port 12 and the exhaust port 13, respectively. Equipped. The intake valve 14 and the exhaust valve 15 are urged in the closing direction (upward in FIG. 1) by return springs 16 and 17, respectively, and cam portions 18a and 19a provided on the outer periphery of the rotating camshafts 18 and 19, respectively. Cam followers 20a and 21a provided rotatably at substantially central portions of the swing arms 20 and 21 are pushed downward, and the swing arm is supported with the top of the pivot mechanism provided on one end side of the swing arms 20 and 21 as a fulcrum. 20 and 21 are configured such that the intake valve 14 and the exhaust valve 15 are pushed downward to open against the urging force of the return springs 16 and 17 at the other end of the swing arms 20 and 21 by swinging. Has been.

[Hydraulic actuator]
The engine 2 includes various hydraulic operation devices (oil supply units) that are operated by the oil pressure of the oil supplied by the engine oil supply device according to the present embodiment.

  For example, the pivot mechanism of the swing arms 20 and 21 of the second and third cylinders located at the center in the cylinder row direction of the engine 2 (the same configuration as the pivot mechanism of the HLA 25 described later) is not shown in detail, but Is provided with a known hydraulic lash adjuster 24 (hereinafter referred to as HLA 24 using an abbreviation of “Hydraulic Lash Adjuster”) that automatically adjusts the valve clearance to zero.

  Moreover, HLA25 with a valve stop mechanism provided with a pivot mechanism is provided with respect to the swing arms 20 and 21 of the first and fourth cylinders located at both ends of the engine 2 in the cylinder row direction. Although the detailed illustration is omitted, the HLA 25 with a valve stop mechanism is a part of all cylinders in the engine 2 in addition to the pivot mechanism configured to be able to automatically adjust the valve clearance to zero like the HLA 24. During the reduced-cylinder operation in which the operation of certain first and fourth cylinders (corresponding to specific cylinders) is stopped, the intake and exhaust valves 14 and 15 of the first and fourth cylinders are stopped (open / close operation is stopped), while all cylinders When all cylinders are operated to operate (four cylinders), a valve stop mechanism that operates (opens and closes) the intake and exhaust valves 14 and 15 of the first and fourth cylinders is provided. The intake and exhaust valves 14 and 15 of the second and third cylinders are operated during both the reduced cylinder operation and the all cylinder operation. Therefore, during the reduced cylinder operation, the intake and exhaust valves 14 and 15 of only the first and fourth cylinders of all the cylinders of the engine 2 are deactivated. During the full cylinder operation, the intake and exhaust valves 14 and 15 of all the cylinders are activated. Will do. Note that the reduced cylinder operation and the all cylinder operation are switched according to the operating state of the engine 2.

  Mounting holes 26 and 27 for inserting and mounting the lower end portion of the HLA 25 with a valve stop mechanism are provided in portions on the intake side and exhaust side corresponding to the first and fourth cylinders in the cylinder head 4, respectively. Yes. In addition, mounting holes similar to the mounting holes 26 and 27 for inserting and mounting the lower end portion of the HLA 24 are provided in portions on the intake side and the exhaust side corresponding to the second and third cylinders in the cylinder head 4. Is provided. Further, the cylinder head 4 is provided with two oil passages 61, 63; 62, 64 communicating with the mounting holes 26, 27 for the HLA 25 with a valve stop mechanism, respectively. The oil passages 61 and 62 supply hydraulic pressure (operating pressure) for operating the valve stop mechanism in the HLA 25 with a valve stop mechanism, and the oil passages 63 and 64 have a valve stop mechanism. The pivot mechanism of the HLA 25 is configured to supply a hydraulic pressure for automatically adjusting the valve clearance to zero. Note that only the oil passages 63 and 64 communicate with the mounting holes for the HLA 24.

  The cylinder block 5 is provided with a main gallery 54 that extends in the cylinder row direction in the side wall on the exhaust side of the cylinder bore 7. An oil jet 28 (oil injection valve) for cooling the piston communicating with the main gallery 54 is provided for each piston 8 in the vicinity of the lower side of the main gallery 54. The oil jet 28 has a nozzle portion 28a disposed on the lower side of the piston 8 and injects engine oil (hereinafter simply referred to as oil) from the nozzle portion 28a toward the back surface of the top portion of the piston 8. It is configured as follows.

  Above each camshaft 18, 19, oil showers 29, 30 formed of pipes are provided, and oil for lubrication from the oil showers 29, 30 is placed below the camshafts 18, 19. The cam portions 18a and 19a, and the contact portions between the swing arms 20 and 21 and the cam followers 20a and 21a, which are located further below, are configured to drop.

  Although not shown in FIG. 1, a hydraulically operated valve characteristic that changes the valve characteristic of at least one of the intake valve 14 and the exhaust valve 15 (both in the present embodiment) by hydraulic operation in all cylinders of the engine 2. A variable valve timing mechanism (hereinafter simply referred to as VVT) as a changing device is provided. VVT has an intake side VVT and an exhaust side VVT. The intake-side VVT and the exhaust-side VVT are also hydraulic actuators like the HLAs 24 and 25, and the configurations thereof are well-known. Therefore, the explanation is omitted, but the intake-side VVT and the exhaust-side VVT are respectively the intake-side and exhaust-side VVT. By supplying and discharging hydraulic pressure to the side advance hydraulic chamber and retard hydraulic chamber, the rotational phase of the camshafts 18 and 19 is shifted relative to the rotational phase of the crankshaft 9, and the intake valve 14 and the exhaust valve 15 are opened. The phase is changed in the advance direction and the retard direction.

[Hydraulic system]
Next, a hydraulic system (oil supply device) 1 for supplying oil to the engine 2 will be described with reference to FIGS. 1 and 2. The hydraulic system 1 includes a variable displacement oil pump 36 (hereinafter referred to as an oil pump 36) driven by the rotation of the crankshaft 9 and an oil supply passage H connected to the oil pump 36.

[Oil pump]
The oil pump 36 is an auxiliary machine that is driven by the engine 2. The oil whose pressure has been increased by the oil pump 36 is guided to the lubrication part of the engine 2 and the hydraulic actuator via the oil supply path H.

  As shown in FIGS. 3 and 4, the oil pump 36 is a variable displacement oil pump that changes the capacity of the oil pump 36 and makes the oil discharge amount of the oil pump 36 variable, with one end opened. And a housing (pump housing) 361 comprising a pump body having a pump housing chamber having a circular cross section inside and a cover member for closing the one end opening of the pump body, and the housing 361 is rotatable. And a drive shaft 362 that passes through a substantially central portion of the pump housing chamber and is rotationally driven by the crankshaft 9, and is rotatably accommodated in the pump housing chamber, and the central portion is coupled to the drive shaft 362. The rotor 363 and the vane 3 accommodated in a plurality of slits formed in the outer peripheral portion of the rotor 363 so as to be freely protruded and retractable. 4 and an outer peripheral side of the pump element are arranged so as to be eccentric with respect to the rotation center of the rotor 363, and together with the rotor 363 and adjacent vanes 364, define a plurality of pump chambers (working chambers) 365. A cam ring 366, a spring 367, which is housed in the pump body and constantly biases the cam ring 366 toward the side where the eccentric amount of the cam ring 366 increases with respect to the rotation center of the rotor 363, and the inner peripheral side of the rotor 363 And a pair of ring members 368 having a smaller diameter than the rotor 363, which are slidably disposed on both side portions.

  The housing 361 discharges oil from the suction passage 361a for supplying oil to the pump chamber 365 accommodated therein, the suction port 361a 'at the end opposite to the pump chamber of the suction passage 361a, and the pump chamber 365. Discharge passage (pump downstream oil passage) 361b and a discharge port 361b 'at the opening end of the discharge passage 361b opposite to the pump chamber.

  Inside the housing 361 is formed a pressure chamber (control hydraulic chamber) 369 defined by an inner peripheral surface of the housing 361, an outer peripheral surface of the cam ring 366, and a seal portion 370 where these surfaces contact each other. An introduction hole 369a that opens to the pressure chamber 369 is provided.

  The oil pump 36 introduces oil into the pressure chamber 369 from the introduction hole 369a, so that the cam ring 366 swings with respect to the fulcrum 361c, and the rotor 363 is eccentric relative to the cam ring 366. That is, the discharge capacity can be changed by changing the volume of the pump chamber 365 according to the pressure of the pressure chamber 369.

  An oil strainer 39 facing the oil pan 6 is connected to the suction port 361 a ′ of the oil pump 36. An oil cooler 38 is disposed in the second oil passage 51 on the downstream side of the oil filter 37, and the oil stored in the oil pan 6 is pumped up by the oil pump 36 through the oil strainer 39, After being filtered by the filter 37 and cooled by the oil cooler 38, it is introduced into the main gallery 54 in the cylinder block 5 and the head gallery 60 in the cylinder head 4.

  The metal bearing for rotatably supporting the crankshaft 9 and the camshafts 18 and 19 and the lubricating and cooling oil supplied to the piston 8, the camshafts 18 and 19 and the like have been cooled and lubricated. Then, it drops into the oil pan 6 through a drain oil passage (not shown) and is recirculated by the oil pump 36.

[Oil supply path]
The oil supply path H communicates with the pump chamber 365 of the oil pump 36 and is connected to the lubrication part of the engine 2 and the hydraulic actuator. An oil filter 37 is disposed on the oil supply passage H on the downstream side of the pump chamber of the oil pump 36.

  The oil supply path H includes a first oil path (pump downstream oil path) 93 that connects the discharge port 361 b ′ of the oil pump 36 and the oil filter 37, and a hydraulic path 50 that is connected to the downstream side of the oil filter 37. ing.

  The pump downstream oil passage connecting the pump chamber 365 of the oil pump 36 and the oil filter 37 is a first oil passage 93 and a discharge passage (pump downstream oil passage provided in the housing 361 of the oil pump 36 described above). ) 361b.

  The hydraulic path 50 includes a pipe, a path drilled in the cylinder head 4, the cylinder block 5, and the like. Specifically, the hydraulic path 50 includes a second oil path 51 extending from the oil filter 37 to the branch point 54b in the cylinder block 5, the main gallery 54 extending in the cylinder row direction in the cylinder block 5, and the branch point 54b. A third oil passage 52 extending to the cylinder head 4, a fourth oil passage extending in the substantially horizontal direction between the intake side and the exhaust side in the cylinder head 4, and a plurality of branches branched from the fourth oil passage in the cylinder head 4 And a head gallery 60 including oil passages 61 to 69.

  The main gallery 54 includes a metal bearing lubrication portion disposed on the oil jet 28 for injecting cooling oil to the back side of the four pistons 8 and five main journals rotatably supporting the crankshaft 9. (Oil supply part) A1 is connected to a lubrication part (oil supply part) A2 of a metal bearing disposed on the crank pin of the crankshaft 9 that rotatably connects the four connecting rods. This main gallery 54 is always supplied with oil.

  On the main gallery 54, a hydraulic pressure path sensor (hydraulic pressure detecting means) 70 for detecting the hydraulic pressure of the main gallery 54 is disposed. The oil pressure sensor 70 is configured to detect the oil pressure of the oil pressure path 50 for supplying oil to the lubrication part of the engine 2 and the oil pressure actuator by the oil pump 36. The hydraulic system 1 includes a plurality of hydraulic sensors in the main gallery 54 and the head gallery 60, for example, around the hydraulic actuator, in addition to the hydraulic sensor 70, and these hydraulic sensors are connected to the hydraulic path 50. It is comprised so that the oil pressure of may be detected.

  In the head gallery 60, since the exhaust side and the intake side have the same configuration, the exhaust side will be described as an example. For example, the oil passage 60A of the head gallery 60 is exhausted via the exhaust side first direction switching valve. It is connected to an advance hydraulic chamber and a retard hydraulic chamber on the exhaust side VVT for changing the opening / closing timing of the valve 15, and is configured to supply oil by controlling the first direction switching valve. . The oil passage 64 is connected to a lubrication part (oil supply part) A3 of a metal bearing disposed in the cam journal of the camshaft 19 on the exhaust side, the HLA 24, and the HLA 25 with a valve stop mechanism. Further, the oil passage 60 </ b> B of the head gallery 60 is connected to an oil shower 30 that supplies lubricating oil to the exhaust-side swing arm 21.

  The oil passage 60C of the head gallery 60 branches into two oil passages 61 and 62 communicating with the mounting holes 26 and 27 for the HLA 25 with a valve stop mechanism. The oil passages 61 and 62 are connected to the valve stop mechanism of the HLA 25 with the valve stop mechanism on the intake side and the exhaust side via the second direction switch valves on the intake side and the exhaust side, respectively. By controlling this, oil is supplied to each valve stop mechanism.

<Features of the hydraulic system>
Here, the hydraulic system 1 according to this embodiment includes a control oil passage 90 that is branched from the above-described discharge passage 361b as a pump downstream oil passage and connected to the pressure chamber 369 of the oil pump 36. Features.

  An oil control valve (control valve) 49 configured to change the oil flow rate of the control oil passage 90 by changing the opening degree is provided on the control oil passage 90. The control oil passage 90 and the oil control valve 49 are integrally formed in the housing 361 of the oil pump 36.

  The control oil passage 90 and the oil control valve 49 are used when starting the oil pump when the engine 2 is started, and when starting the engine 2, a normal control (feedback control) SB is described later. Used for. Hereinafter, each configuration will be described in detail.

[Control oil passage]
As shown in FIGS. 5 and 6, the upstream control oil passage 90 a of the control oil passage 90 is branched from the discharge passage 361 b of the housing 361 and connected to an oil control valve 49 integrally formed with the housing 361. ing.

  The oil sent from the pump chamber 365 of the oil pump 36 to the discharge passage 361b and introduced into the oil control valve 49 via the upstream control oil passage 90a passes through the oil control valve 49 and then is shown in FIG. Then, the oil is introduced into the pressure chamber 369 of the oil pump 36 through the control oil passage 90 b on the downstream side of the control oil passage 90. As shown in FIG. 7, the downstream control oil passage 90b is connected to a pressure chamber 369 of the oil pump 36 via an oil passage formed by a valve housing 496 of the oil control valve 49 and a spool valve 491. Yes.

  That is, in the present embodiment, the control oil passage 90 functions as a leak passage for preventing damage to the oil filter 37 when the starting control SA is performed, and when the normal control SB is performed. It functions as a passage for controlling the oil discharge amount of the oil pump 36. By adopting this configuration, the leak passage and the control passage can be made common, so that the oil pump 36 and the hydraulic system 1 can be made compact.

[Oil control valve]
As shown in FIG. 8, the oil control valve 49 includes a valve housing 496, a spool valve 491 housed in the valve housing 496, a filter 494 formed in the valve housing 496 for filtering oil, and electromagnetic force. And a plunger 495 for displacing the spool valve 491 in the arrow 497 direction by the electromagnetic force of the coil 493 and a valve spring 492. The spool valve moves in the direction of arrow 497, whereby the opening of the oil flow path of the oil control valve 49 is changed. Then, the flow passage cross-sectional area of the oil introduced from the upstream control oil passage 90a is changed, and the oil passage flow rate is changed.

  The oil control valve 49 is not limited to this configuration, and an electromagnetic control valve having a well-known configuration can be used as appropriate.

[IG-ON / OFF detection means]
As shown in FIG. 2, the hydraulic system 1 according to the present embodiment includes an ignition-ON / OFF detection means as a start request detection means for detecting an ignition switch ON signal (start request) when the engine 2 is started. 105 (hereinafter referred to as IG-ON / OFF detection means). In addition, this structure is good also as a structure which detects the starting request | requirement of the oil pump 36 instead of the starting request | requirement of the engine 2. FIG.

[Oil temperature detection means]
As shown in FIG. 2, oil temperature detection means (fluid temperature detection means) 92 for detecting the oil temperature upstream of the oil filter 37 is disposed on the first oil passage 93. The oil temperature detection means 92 may be configured to be installed on the discharge passage 361b of the oil pump 36, for example, to be disposed in the housing 361 so as to detect the oil temperature inside the discharge passage 361b.

[control unit]
The control unit (control unit) 100 is a control device based on a well-known microcomputer, and as shown in FIG. 2, a hydraulic sensor 70, an oil temperature detecting means 92, an engine speed detecting means 102, an accelerator opening degree. A signal input unit 100a that inputs detection signals from various sensors such as the detection unit 103, the gear stage detection unit 104, and the IG-ON / OFF detection unit 105; and an arithmetic unit (estimation unit) 100b that performs arithmetic processing related to control. A signal output unit 100c that outputs a control signal to a device to be controlled, such as the oil control valve 49, and a program and data necessary for control (a hydraulic control map described later, viscosity characteristics in the second embodiment, etc.) And a storage unit 100d. The operation of the engine 2 is controlled by the control unit 100. Detection information from various sensors that detect the operating state of the engine 2 is input to the control unit 100.

  The control unit 100 supplies a duty ratio control signal to the oil control valve 49, controls the opening degree of the oil control valve 49, and adjusts the passage flow rate to supply the pressure chamber 369 of the oil pump 36. To control the hydraulic pressure. The flow rate (discharge amount) of the oil pump 36 is controlled by controlling the amount of eccentricity of the cam ring 366 and the amount of change in the internal volume of the pump chamber 365 by the hydraulic pressure of the pressure chamber 369. Here, since the oil pump 36 is driven by the crankshaft 9 of the engine 2, the flow rate (discharge amount) of the oil pump 36 is proportional to the engine rotation speed.

  Thus, the control unit 100 configures a control unit that controls the discharge amount of the oil pump 36 by changing the capacity of the oil pump 36.

[Normal control]
The hydraulic system 1 supplies oil to a plurality of lubrication units and hydraulic actuators by a single oil pump 36, and the required hydraulic pressure required by each lubrication unit and each hydraulic actuator depends on the operating state of the engine 2. Change. Therefore, in order to obtain a hydraulic pressure that is required for all the lubrication units and the hydraulic actuators in all operating states of the engine 2, the oil pump 36 is required for each of the hydraulic actuators for each operating state of the engine 2. Therefore, it is necessary to set a hydraulic pressure equal to or higher than the highest required hydraulic pressure to a target hydraulic pressure corresponding to the operating state of the engine 2. For this purpose, the required hydraulic pressures of the valve stop mechanism, the oil jet 28, the journal of the crankshaft 9, etc., the intake side VVT and the exhaust side VVT are required. What is necessary is just to set target oil pressure so that it may satisfy | fill. This is because, if the target oil pressure is set in this way, other hydraulic actuators having a relatively low required oil pressure naturally satisfy the required oil pressure.

  Hydraulic control in which a temporary target hydraulic pressure in the operating state is set in advance based on the highest required hydraulic pressure among the required hydraulic pressures of the intake side VVT, the exhaust side VVT, the metal bearing, and the oil jet 28 for each operating state of the engine 2. The map is stored in the storage unit 100d of the control unit 100. The control unit 100 reads the temporary target oil pressure corresponding to the operating state of the engine 2 from the oil pressure control map, and targets the higher one of the read temporary target oil pressure and the required oil pressure of the valve stop mechanism of the HLA 25. Set to hydraulic pressure. The control unit 100 reads the oil pressure (actual oil pressure) detected by the corresponding oil pressure sensor, and adjusts the opening of the oil control valve 49 so that the oil pressure becomes the target oil pressure. The hydraulic feedback control for controlling the discharge amount is executed as the normal control SB.

[Control at start-up]
When the ON signal is detected by the IG-ON / OFF detection means 105, the control unit 100 detects the oil temperature detection value (fluid temperature detection value) detected by the oil temperature detection means 92 before starting the driving of the oil pump 36. ), And when the detected oil temperature value detected by the oil temperature detecting means 92 is equal to or lower than a predetermined value, the opening degree of the oil control valve 49 is set to a predetermined ratio so that the oil can flow through the control oil passage 90. The above starting control SA is performed.

  On the other hand, when the detected oil temperature value detected by the oil temperature detecting means 92 exceeds the predetermined value, the control unit 100 does not perform the starting control SA.

  The start-up control SA is required when the outside air temperature is extremely cold. In such a case, the temperature of the engine oil is almost the same as the outside air temperature, and the oil viscosity is relatively high. . Specifically, for example, when the oil temperature detected by the oil temperature detecting means 92 is −10 ° C. or less, the start-up control SA is performed.

  Then, when the detected oil temperature value of the oil before flowing into the oil filter 37 is a low temperature and high viscosity less than or equal to a predetermined value, the oil is circulated through the control oil passage 90 at the same time when the oil pump 36 starts to be driven. By allowing the oil to flow into the pressure chamber 369, the pump discharge amount becomes smaller than the maximum discharge amount at the same time when the oil pump is started, and the oil flow rate flowing into the oil filter 37 is reduced. 37 can be prevented from being damaged.

  In the start-up control SA, when the oil temperature detection value detected by the oil temperature detection means 92 is equal to or lower than the predetermined value, the oil control valve 49 is opened more than when the oil temperature detection value exceeds the predetermined value. You may comprise so that a degree may become large.

  Further, the control unit 100 reduces the opening of the oil control valve 49 in accordance with, for example, an increase in the oil temperature detection value of the oil temperature detecting means 92 after the oil pump 36 starts driving in the start-up control SA. It is possible to reduce the oil flow rate in the control oil passage 90 and increase the oil flow rate flowing into the oil filter 37. Thus, oil can be supplied to the hydraulic path 50 on the downstream side of the oil filter 37 by increasing the oil flow rate to the oil filter 37 as the oil temperature rises while preventing the oil filter 37 from being damaged. it can.

[Control flow of hydraulic system]
FIG. 9 shows a control flow of the hydraulic system 1 according to the present embodiment.

  First, the ignition switch ON signal detected when the engine 2 is started, which is detected by the IG-ON / OFF detection means 105, is read (S1).

  Next, the detected oil temperature value of the oil temperature detecting means 92 arranged on the first oil passage 93 is read (S2).

  Then, it is determined whether the oil temperature detection value is equal to or less than a predetermined value (S3).

  When the detected oil temperature value is equal to or lower than the predetermined value, the start time control SA including the following steps S4 to S7 is executed.

  That is, the opening degree of the oil control valve 49 is determined based on the detected oil temperature value (S4), and the oil control valve 49 is operated (S5) so that oil can flow into the pressure chamber 369. Thus, the oil discharge amount of the oil pump 36 is controlled to be smaller than the maximum discharge amount.

  Then, driving of the oil pump 36 is started.

  Thereafter, the main gallery hydraulic pressure detection value of the hydraulic sensor 70 disposed on the main gallery 54 is read (S6), and it is determined whether or not the main gallery hydraulic pressure detection value of the hydraulic sensor 70 is equal to or greater than a predetermined value (S7). .

  When it is determined that the main gallery hydraulic pressure detection value is equal to or greater than the predetermined value, it is confirmed that the hydraulic pressure has been applied to the end of the oil supply passage H of the engine 2, so the start-up control SA is terminated and the normal control SB is restored. (S8).

  On the other hand, if it is determined in S7 that the main gallery hydraulic pressure detection value is not equal to or greater than the predetermined value, that is, less than the predetermined value, the hydraulic pressure is not applied to the end of the oil supply passage H of the engine 2, and therefore the main gallery hydraulic pressure detection value. Until it is determined that the value is equal to or greater than a predetermined value, the start-time control SA from Steps S4 to S7 is repeatedly executed.

  Since the predetermined value of the main gallery hydraulic pressure detection value varies depending on the length of the oil supply path H, that is, the engine model, the value obtained in advance through experiments or the like is stored in the storage unit 100d of the control unit 100 as the predetermined value. The determination is made by comparing the main gallery oil pressure detection value detected by the oil pressure sensor 70 with the predetermined value. Instead of determining whether the main gallery hydraulic pressure detection value is equal to or greater than a predetermined value, the main gallery hydraulic pressure detection value is substantially constant and stable, for example, a predetermined time or more elapses at a value within 10% around the predetermined value. You may make it judge with a thing.

  In the normal control SB, the operation state of the engine 2 is read (S9), and based on the operation state, the target hydraulic pressure that is the control target of the oil control valve 49 is determined (S10), and the corresponding control on the hydraulic path 50 is performed. The opening degree of the oil control valve 49 is controlled so that the oil pressure detected by the oil pressure sensor becomes the target oil pressure (S11).

  When it is determined in step S3 that the detected oil temperature value exceeds the predetermined value, the start-up control SA is not performed, and the normal control SB in steps S9 to S11 is performed after the oil pump 36 starts driving. Is done.

  Then, the normal control SB of S9 to S11 is repeatedly performed until the ignition switch OFF signal accompanying the stop of the engine 2 is detected by the IG-ON / OFF detection means 105.

<Functional effects of hydraulic system features>
FIG. 10 shows a case where the engine 2 is maintained at about 800 rpm after the engine speed reaches about 800 rpm (a value set not to be stalled) in an idle operation state from the start of cranking of the engine 2, that is, in a state where the accelerator is not stepped on. 4 shows the change over time in the oil pressure upstream of the oil filter 37, the change over time in the engine speed correlated with the oil pump speed, and the change over time in the oil pressure detection value of the oil pressure sensor 70 disposed on the main gallery 54. . In the graph, a point P indicates a point in time when the engine speed reaches about 800 rpm, and indicates an engine start completion, that is, a cranking end point. Point Q indicates a point in time at which the hydraulic pressure of the main gallery 54 reaches the minimum hydraulic pressure required for the lubricating portion (crank journal, cam journal, etc.).

  As shown by the broken line in FIG. 10, in the conventional hydraulic system shown in FIG. 13, a so-called spike hydraulic pressure is generated on the upstream side of the oil filter 37, in which the oil pressure suddenly increases when the oil pump 36 is started when the engine is started. To do. The spike hydraulic pressure is caused by the fact that the oil has a low temperature and high viscosity at the time of starting the oil pump at the time of starting the engine, and if a large amount of such low temperature and high viscosity oil flows into the oil filter 37, the oil filter 37 can be damaged. Therefore, a leak passage is provided upstream of the oil filter 37 in the related art, and excess oil leaks to the oil pan 6 to reduce the oil pressure and protect the oil filter 37.

  According to the configuration of the present embodiment, as shown by the solid line in FIG. 10, the hydraulic pressure on the upstream side of the oil filter 37 is increased with the start of driving of the oil pump 36, but a rapid hydraulic pressure such as spike hydraulic pressure is observed. No increase is observed. Therefore, by controlling the opening degree of the oil control valve 49 by the start-time control SA, the oil flow rate in the control oil passage 90 is increased to reduce the oil flow rate to the oil filter 37 and prevent the oil filter 37 from being damaged. Can do.

  As shown in FIG. 10, the hydraulic pressure of the main gallery 54 rises later than the hydraulic pressure on the upstream side of the oil filter 37 by the distance from the oil pump 36 and reaches the minimum hydraulic pressure necessary for the lubrication unit. It can be seen that the oil pressure on the upstream side of the oil filter 37 is stabilized at a substantially constant value at the time point Q to be performed.

  Therefore, according to this configuration, when the detected value of the hydraulic sensor 70 arranged on the main gallery 54 reaches a predetermined value, for example, the hydraulic pressure at the point Q shown in FIG. 10, YES in step S7 shown in FIG. Can be determined to return to the normal control SB from the starting control SA. Then, during the period from the start of the engine until the predetermined main gallery hydraulic pressure detection value is reached, the start-up control SA is performed to suppress damage to the oil filter 37 and after the predetermined hydraulic pressure detection value is reached. By changing to the normal control SB of the oil pump 36, the hydraulic pressure of the hydraulic path 50 can be efficiently controlled.

  In this configuration, the hydraulic system 1 can be made compact by integrally forming the control oil passage 90 and the oil control valve 49 in the housing 361 of the oil pump 36. Further, since the oil path length of the control oil path 90 can be shortened compared to drilling the control oil path 90 in other engine parts, the pipe resistance of the oil path is reduced. Then, by raising the hydraulic pressure of the pressure chamber 369, the electromagnetic control valve can be controlled to a lower discharge amount even at the same opening degree, so that the pump work can be reduced. Further, the control oil passage 90 is connected to the pressure chamber 369 of the oil pump 36 through the oil control valve 49, so that excess oil is directly introduced into the pressure chamber 369 of the oil pump 36 without leaking to the oil pan 6. As a result, the pump work can be reduced.

(Second Embodiment)
Hereinafter, other embodiments according to the present disclosure will be described in detail. In the description of these embodiments, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the first embodiment, the control unit 100 is configured to perform the start-up control SA based on the oil temperature detection value detected by the oil temperature detection means 92. In the present embodiment, however, the control unit 100 starts from the oil temperature detection value. The viscosity of the oil is estimated, and the control unit 100 is configured to perform start-up control SA based on the estimated viscosity value of the oil. That is, the storage unit 100d of the control unit 100 stores in advance the viscosity characteristics of oil (the relationship of the viscosity with respect to the oil temperature).

  Then, as shown in FIG. 11, the calculation unit of the control unit 100 calculates the oil viscosity based on the oil temperature detection value detected by the oil temperature detection means 92 and the viscosity characteristic stored in the storage unit 100d. An estimated viscosity value is obtained by estimation (S31).

  Next, the control unit 100 determines whether or not the estimated viscosity value obtained by the calculation unit is greater than or equal to a predetermined value (S32).

  When the estimated viscosity value is equal to or greater than the predetermined value, the start-time control SA is executed. On the other hand, when the estimated viscosity value is less than the predetermined value, the start-time control SA is not executed and the normal control SB is executed. .

  According to this configuration, the oil temperature of the oil before flowing into the oil filter 37 is detected, and based on the obtained oil temperature detection value and the viscosity characteristics of the oil stored in the storage unit 100d in advance, When the viscosity is estimated and the estimated viscosity is a high viscosity equal to or higher than a predetermined value, the oil flow rate in the control oil passage 90 is increased to a predetermined amount or more to reduce the oil flow rate flowing into the oil filter 37, and the oil filter 37 can be prevented from being damaged.

(Third embodiment)
In the first and second embodiments, the startup control SA is performed when the oil temperature detection value of the oil detected by the oil temperature detection unit 92 is equal to or less than a predetermined value.

  On the other hand, instead of the configuration using the oil temperature of the oil, a water jacket (water cooling unit) (not shown) provided around the cylinder head 4 of the engine 2 shown in FIG. The cooling water temperature may be used.

  That is, when the outside air temperature that requires the start-time control SA is extremely cold, the water temperature of the water jacket cooling water is considered to be low, and the oil viscosity is relatively high under such circumstances. it is conceivable that.

  Therefore, for example, the water temperature is detected by a water temperature detecting means configured to detect the water temperature of the cooling water in the water jacket, and when the water temperature is a predetermined value or less, specifically, for example, 0 ° C. or less, or the outside air temperature. When the estimated viscosity value estimated based on the above is equal to or greater than a predetermined value, the starting control SA can be performed. When the water temperature exceeds a predetermined value or when the estimated viscosity value is less than the predetermined value, the normal control SB can be performed without performing the start-time control SA.

(Fourth embodiment)
In the third embodiment, the temperature of the cooling water of the water jacket is used as the temperature of the fluid that contacts the vehicle member. However, for example, the atmospheric air outside the vehicle that contacts the exterior member of the vehicle such as a vehicle door is used. It is good also as a structure which uses temperature, ie, external temperature.

  Specifically, for example, an outside air temperature detecting means is provided on a vehicle door or the like to detect the outside air temperature, and when the outside air temperature is a predetermined value or less, specifically, for example, 0 ° C. or less, or estimated based on the outside air temperature When the estimated viscosity value is greater than or equal to a predetermined value, the starting control SA can be performed. When the outside air temperature exceeds the predetermined value or the estimated viscosity value is less than the predetermined value, the normal control SB can be performed without performing the starting control SA.

(Fifth embodiment)
In the above-described embodiment, the temperature of the fluid contacting the vehicle member is detected, and the start-up control SA is performed when the fluid temperature is equal to or lower than a predetermined value.

  On the other hand, as shown in FIG. 12, the oil pump 36 is driven when the ignition switch ON signal is detected by the IG-ON / OFF detection means 105 without detecting the temperature of the fluid contacting the vehicle member. It is good also as a structure which performs start-up control SA before the start.

  In this configuration, the start-time control SA is forcibly performed at the start of driving of the oil pump 36 when the engine 2 is started. Thereby, it is not necessary to provide the fluid temperature detecting means on the vehicle member, and the breakage of the oil filter 37 can be effectively suppressed with a simple configuration.

(Sixth embodiment)
In the above embodiment, the start-up control SA is performed until the hydraulic pressure detection value of the main gallery 54 detected by the hydraulic sensor 70 becomes a predetermined value or more in step S7 shown in FIGS. It was the structure which returns to normal control SB as a trigger when the hydraulic pressure of this becomes more than predetermined value.

  As a trigger for switching from the start time control SA to the normal control SB, as shown in FIG. 10, the engine speed (engine speed detection value) detected by the engine speed detection means 102 is a predetermined speed such as 800 rpm. The cranking end point that reaches the number, that is, the point P as a trigger, may be configured to return to the normal control SB when the predetermined number of revolutions is reached.

  Furthermore, the time when the accelerator is depressed, that is, the time when the accelerator opening detected by the accelerator opening detecting means 103 shown in FIG.

  Further, a signal detected by the gear position detection means 104 may be used as a trigger.

  In addition, timer control can be performed so that the start-time control SA is switched to the normal control SB after a predetermined time has elapsed from the start of driving the oil pump at the time of engine start.

(Seventh embodiment)
In the above embodiment, the start-up control SA has a configuration in which the opening of the oil control valve 49 is set to a predetermined ratio or more so that oil can flow through the control oil passage 90.

  On the other hand, the opening degree of the oil control valve 49 may be maximized so that the oil flow rate in the control oil passage 90 is maximized in the starting control SA. Specifically, for example, the start-time control SA may be configured to maximize the oil control valve 49 and maintain it until the end of the start-time control SA in steps S4 and S5 in FIGS. . With this configuration, it is possible to prevent the oil filter 37 from being damaged with a simple configuration.

(Other embodiments)
In the above embodiment, the control oil passage 90 and the oil control valve 49 are integrally formed with the housing 361 in the first embodiment, but may be configured to be attached to the housing 361 as separate parts. Thereby, it becomes possible to easily attach to various oil pumps 36.

  The engine 2 is not limited to an inline 4-cylinder gasoline engine, and may be any engine. For example, a diesel engine may be used.

1 Hydraulic system (oil supply device)
2 Engine 4 Cylinder head 36 Oil pump 37 Oil filter 49 Oil control valve (control valve)
50 Hydraulic path 51 Second oil path 52 Third oil path 54 Main gallery 54b Branch point 60 Head gallery 70 Oil pressure sensor (oil pressure detecting means)
90 Control oil passage 90a Upstream control oil passage 90b Downstream control oil passage 92 Oil temperature detection means (fluid temperature detection means)
93 1st oil passage (pump downstream oil passage)
100 Control unit (control unit)
100b Calculation unit (estimation unit)
100d storage unit 105 IG-ON / OFF detection means (start request detection means)
361 Housing (pump housing)
361b Discharge passage (pump downstream oil passage)
365 Pump room (working room)
369 Pressure chamber (control hydraulic chamber)
H Refueling path

Claims (10)

A variable capacity oil pump configured to have a working chamber and a control hydraulic chamber, and configured to change a discharge capacity by changing a volume of the working chamber according to a pressure of the control hydraulic chamber;
An oil supply passage that communicates with the working chamber of the oil pump and is connected to an oil supply section provided downstream of the oil pump;
An oil filter disposed on the oil supply path and downstream of the working chamber of the oil pump;
An oil supply device for an engine equipped with
The oil supply path is
A pump downstream oil passage connecting the working chamber of the oil pump and the oil filter;
A control oil passage branched from the pump downstream oil passage and connected to a control hydraulic chamber of the oil pump;
With
A control valve provided on the control oil passage and configured to change an oil flow rate of the control oil passage by changing an opening;
A control unit for controlling the opening of the control valve;
Start request detecting means for detecting a start request of the engine or the oil pump;
With
When the start request detecting unit detects the start request for the engine or the oil pump, the control unit allows oil to flow through the control oil passage before starting the oil pump drive. An engine oil supply apparatus that performs start-up control so that the opening degree of the control valve is a predetermined ratio or more. A variable capacity oil pump configured to have a working chamber and a control hydraulic chamber, and configured to change a discharge capacity by changing a volume of the working chamber according to a pressure of the control hydraulic chamber;
An oil supply passage that communicates with the working chamber of the oil pump and is connected to an oil supply section provided downstream of the oil pump;
An oil filter disposed on the oil supply path and downstream of the working chamber of the oil pump;
An oil supply device for an engine equipped with
The oil supply path is
A pump downstream oil passage connecting the working chamber of the oil pump and the oil filter;
A control oil passage branched from the pump downstream oil passage and connected to a control hydraulic chamber of the oil pump;
With
A control valve provided on the control oil passage and configured to change an oil flow rate of the control oil passage by changing an opening;
A control unit for controlling the opening of the control valve;
Start request detecting means for detecting a start request of the engine or the oil pump;
Fluid temperature detecting means installed on a member of the engine or a vehicle on which the engine is mounted and detecting a temperature of a fluid contacting the engine or the member;
With
The controller is
When the start request of the engine or the oil pump is detected by the start request detecting means, before the start of driving the oil pump, the fluid temperature detection value detected by the fluid temperature detecting means is read,
When the control valve is opened to a predetermined ratio or more so that oil can flow through the control oil passage when the fluid temperature detection value detected by the fluid temperature detection means is not more than a predetermined value. An oil supply device for an engine characterized by performing control. A variable capacity oil pump configured to have a working chamber and a control hydraulic chamber, and configured to change a discharge capacity by changing a volume of the working chamber according to a pressure of the control hydraulic chamber;
An oil supply passage that communicates with the working chamber of the oil pump and is connected to an oil supply section provided downstream of the oil pump;
An oil filter disposed on the oil supply path and downstream of the working chamber of the oil pump;
An oil supply device for an engine equipped with
The oil supply path is
A pump downstream oil passage connecting the working chamber of the oil pump and the oil filter;
A control oil passage branched from the pump downstream oil passage and connected to a control hydraulic chamber of the oil pump;
With
A control valve provided on the control oil passage and configured to change an oil flow rate of the control oil passage by changing an opening;
A control unit for controlling the opening of the control valve;
Start request detecting means for detecting a start request of the engine or the oil pump;
Fluid temperature detecting means installed on a member of the engine or a vehicle on which the engine is mounted and detecting a temperature of a fluid contacting the engine or the member;
With
The controller is
A storage unit for storing in advance the relationship of the viscosity of the oil to the temperature of the fluid;
Based on the fluid temperature detection value detected by the fluid temperature detection means and the relationship between the fluid temperature and the viscosity stored in the storage unit, an estimation unit that estimates the viscosity of the oil and obtains a viscosity estimation value;
With
The controller is
When the start request of the engine or the oil pump is detected by the start request detecting means, the fluid temperature detection value detected by the fluid temperature detecting means is read before starting the oil pump,
When the estimated viscosity value estimated by the estimation unit based on the fluid temperature detection value and the relationship between the fluid temperature and the viscosity is greater than or equal to a predetermined value, the oil can flow through the control oil passage. An engine oil supply device that performs start-up control so that an opening degree of a control valve is a predetermined ratio or more. In claim 2 or 3,
The member is the pump downstream oil passage,
The fluid is oil flowing through the pump downstream oil passage,
The engine oil supply apparatus according to claim 1, wherein the fluid temperature detection means is an oil temperature detection means configured to detect an oil temperature upstream of the oil filter. In claim 2 or 3,
The member is a water cooling part of the engine,
The fluid is cooling water of the water cooling unit,
The engine oil supply device according to claim 1, wherein the fluid temperature detecting means is a water temperature detecting means configured to detect a water temperature of the cooling water of the water cooling section. In claim 2 or 3,
The member is an exterior member of the vehicle,
The fluid is the atmosphere outside the vehicle;
The engine oil supply apparatus according to claim 1, wherein the fluid temperature detecting means is an outside air temperature detecting means configured to detect an outside air temperature outside the vehicle. In any one of Claims 1 thru | or 6,
The engine oil supply device, wherein the control unit maximizes an opening of the control valve in the start-up control. In any one of Claims 1 thru | or 7,
The oil pump includes a pump housing that houses the working chamber and has a discharge port for discharging oil from the working chamber,
The pump downstream oil passage is provided in the pump housing, and includes a discharge passage that connects the working chamber and the discharge port,
The control oil passage is branched from the discharge passage,
The oil supply device for an engine, wherein the control oil passage and the control valve are formed integrally with the pump housing. In any one of Claims 1 thru | or 8,
The oil supply path has a hydraulic path that communicates with the downstream side of the oil filter and is connected to the oil supply section.
A hydraulic pressure detecting means configured to detect a hydraulic pressure of the hydraulic pressure path;
The controller is
When the start-up control is not performed, feedback control is performed to adjust the oil discharge amount of the oil pump by adjusting the opening of the control valve so that the hydraulic pressure in the hydraulic path becomes the target hydraulic pressure. Is composed of
When performing the start-time control, the engine oil supply is switched from the start-time control to the feedback control when the detected oil pressure detected by the oil pressure detecting means becomes a predetermined value or more. apparatus. In any one of Claims 1 thru | or 8,
The oil supply path has a hydraulic path that communicates with the downstream side of the oil filter and is connected to the oil supply section.
An engine speed detecting means configured to detect an engine speed of the engine;
The controller is
When the start-up control is not performed, feedback control is performed to adjust the oil discharge amount of the oil pump by adjusting the opening of the control valve so that the hydraulic pressure in the hydraulic path becomes the target hydraulic pressure. Is composed of
When performing the start time control, when the engine speed detection value detected by the engine speed detection means becomes equal to or higher than a predetermined speed, the start time control is switched to the feedback control. Oil supply device for the engine.