CN110966062B - Control system and control method for hydraulic variable valve - Google Patents
Control system and control method for hydraulic variable valve Download PDFInfo
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- CN110966062B CN110966062B CN201811156115.4A CN201811156115A CN110966062B CN 110966062 B CN110966062 B CN 110966062B CN 201811156115 A CN201811156115 A CN 201811156115A CN 110966062 B CN110966062 B CN 110966062B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/3443—Solenoid driven oil control valves
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Control systems and control methods for hydraulically variable valves are disclosed. The present invention relates to a control system for a hydraulic variable valve. The control system may include: an OCV configured with a housing, a flow passage defined in the housing, a main port, first and second discharge ports, a valve spool, and a relief valve; a main line connecting the main port and the oil pump to each other; a control line connecting the control port and the slack adjuster to each other; an orifice disposed between the main line and the control line; and a controller that controls the OCVs to allow at least one combination of the main port and the first discharge port, the control port and the second discharge port, and the main port and the control port to communicate with each other.
Description
Technical Field
The present disclosure relates to control systems and control methods for hydraulically variable valves.
Background
The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.
An internal combustion engine is an engine that generates power by receiving fuel and air from outside the engine and combusting the fuel and air in a combustion chamber. The internal combustion engine generally has an intake valve through which fuel and air are drawn into a combustion chamber and an exhaust valve through which combustion gas is discharged from the combustion chamber, wherein the intake valve and the exhaust valve are configured to be opened and closed by rotation of a camshaft that rotates as a crankshaft rotates.
To increase the efficiency of the engine, the timing of the opening and closing of the valves may be varied depending on the level of engine RPM and the level of engine load, depending on the operating conditions of the vehicle.
The timing of the opening and closing of the intake valve may affect the charging efficiency such that the valve overlap period increases when the intake valve is pre-opened. Therefore, at high engine speeds, the inertia of the intake air flow and the exhaust gas flow can be fully used, resulting in an increase in volumetric efficiency; at low engine speeds, however, the amount of residual gases increases, resulting in a reduction in volumetric efficiency and an increase in Hydrocarbon (HC) emissions.
A technique of controlling an appropriate valve timing depending on a driving condition of an engine has been developed and applied, whereby a valve overlap period of a camshaft is not determined according to rotation of a crankshaft but has a preset displacement angle, which is called a Continuously Variable Valve Timing (CVVT) system.
The CVVT system is a system for continuously changing the timing of opening and closing of intake and exhaust valves by changing the rotational phases of an intake camshaft and an exhaust camshaft depending on the engine RPM and the vehicle load state, that is, a system for changing the valve overlap, and aims to reduce exhaust, improve performance, and stabilize idling.
Here, the valve timing is a timing of opening or closing of the intake valve and the exhaust valve. The intake process is a process in which a fresh air-fuel mixture is forcibly drawn until the intake valve is opened and closed, and the exhaust process is a process in which combustion gas is forcibly discharged until the exhaust valve is opened and closed. The timing of the opening and closing of the valves typically affects the performance of the engine.
Further, the valve overlap is a period in which both the intake valve and the exhaust valve are open at the same time. In the case of a typical engine, once the valve overlap is set, the set valve overlap is used throughout the engine speed region, which we have found may be disadvantageous in the low engine speed region or the high engine speed region.
Therefore, controlling the valve overlap according to the engine load may result in an increase in engine output, and in this way controlling the valve overlap according to the engine load is a CVVT system.
The components of the CVVT system may include a continuously variable valve timing unit, an Oil Control Valve (OCV) as an oil supply device, an Oil Temperature Sensor (OTS), an oil control valve filter, an oil passage, an auto tensioner, and the like. The continuously variable valve timing unit may be mounted on the exhaust camshaft, and may be configured such that a housing and a rotor are disposed therein and an advance chamber and a retard chamber are disposed between the housing and the rotor vane, wherein engine oil flows in through the OCV to move the rotor vane.
Further, the OCV is a component of the CCVT system, and is used to control the timing of opening and closing of the valve by changing the direction in the fluid path of the engine oil that is supplied from the oil pump and flows to the camshaft under the control of an Engine Control Unit (ECU).
The density of the engine oil, which is the working fluid of the continuously variable valve timing unit, changes depending on the temperature, so that the OTS functions as a sensor that compensates for the amount of density change depending on the temperature. Before the engine oil flows into the OCV, the OTS measures the temperature of the engine oil and transmits the measured temperature to the ECU, and the ECU drives the OCV for correction.
The oil control valve filter is used to filter impurities from engine oil flowing into the OCV, and the auto tensioner is a tension adjusting device of a chain for connecting a sprocket of an exhaust camshaft mounted with the CVVT and a sprocket of an intake camshaft to each other. The automatic tensioner prevents delays or deviations in response from occurring in the CVVT system, thereby providing performance stability.
We have discovered and disclosed an OCV that controls oil pressure to adjust it for operating conditions while achieving a Cylinder Deactivation (CDA) function that is not proposed in the related art.
The foregoing is intended only to aid in understanding the background of the disclosure and is not intended to imply that the disclosure is within the knowledge of one skilled in the art to which it pertains.
Disclosure of Invention
Further areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure.
In one aspect, the present disclosure provides a control system and control method for a hydraulically variable valve in which engine oil pressure is controlled to adjust for operating conditions of a vehicle while implementing CDA functions by using a single OCV.
According to one aspect of the present invention, there is provided a control system for a hydraulically variable valve, the control system comprising: an OCV configured with a housing defining a flow passage therein, a main port provided on an outer peripheral surface of the housing and causing the flow passage and an oil pump to communicate with each other, first and second discharge ports provided on the outer peripheral surface of the housing and causing the flow passage and a lash adjuster to communicate with each other, a spool (spool) moved by a solenoid along the flow passage to open and close the main port, a control port, and the first and second discharge ports, and a relief valve provided in the flow passage at a portion where the control port and the second discharge port are connected to each other and causing a pressure on a control port side to be maintained at a predetermined pressure; a main line connecting the main port and the oil pump to each other; a control line connecting the control line and the slack adjuster to each other; an orifice disposed between the main line and the control line; and a controller that controls the OCVs such that at least one combination of the main port and the first discharge port, the control port and the second discharge port, and the main port and the control port communicate with each other.
The controller may control the OCVs in one of a first mode in which the control port and the second discharge port communicate with each other while the main port and the first discharge port communicate with each other, a second mode in which the main port and the second discharge port communicate with each other, and a third mode; in the second mode, the main port and the first discharge port are closed while the control port and the second discharge port are communicated with each other; and in the third mode, the first and second discharge ports are closed while the main port and the control port are communicated with each other.
The controller may control the OCV in the first mode to adjust the oil pressure in the main line, may control the OCV in the second mode to maintain the oil pressure in the main line at an increased or maximum pressure, and may control the OCV in the third mode when the lash adjuster is to be driven, depending on whether the hydraulic control mechanism is operated.
When the OCV is controlled in the first mode, the controller may control the OCV such that an opening degree of the first discharge port increases when an oil pressure in the main line is higher than a reference region; and the opening degree of the first discharge port is decreased when the oil pressure in the main line is lower than the reference region.
When controlling the OCV in the first mode, the controller may set the reference region to a first minimum or reduced oil pressure region when the hydraulic control mechanism is operated, and may set the reference region to a second reduced oil pressure region lower than the first reduced oil pressure region when the hydraulic control mechanism is not operated.
The OCV may be configured such that the first discharge port, the main port, the control port, and the second discharge port are formed on the outer circumferential surface of the housing to be sequentially arranged in a downward direction or a reverse direction, and the valve spool may be normally positioned at an initial point such that the control port and the second discharge port communicate with each other via the relief valve while the main port and the first discharge port communicate with each other.
The valve spool may have a first end coupled to an armature moved by the solenoid and a second end coupled to a compression spring providing elasticity to the valve spool, whereby the valve spool is normally positioned at the initial point.
The controller may not drive the solenoid when the OCV is controlled in the first mode; when controlling the OCV in the second mode, the controller may drive the solenoid by a first set value such that the spool moves from the initial point to a first point; and when the OCV is controlled in the third mode, the controller may drive the solenoid by a second set value that is greater than the first set value such that the spool moves from the initial point to a second point.
According to another aspect of the present invention, there is provided a control method for a hydraulic variable valve, the control method including: comparing, by the controller, the oil pressure in the main line with a reference zone; and controlling, by the controller, the OCV in the first mode as a result of comparing the oil pressure in the main line with the reference zone such that an opening degree of a first discharge port is maintained when the oil pressure in the main line is included in the reference zone, the opening degree of the first discharge port is increased when the oil pressure in the main line is lower than the reference zone, and the opening degree of the first discharge port is decreased when the oil pressure in the main line is higher than the reference zone.
The control method may further include checking, by the controller, whether the lash adjuster is to be driven before comparing the oil pressure in the main line with the reference region, wherein the controller may control the OCV in a third mode when the lash adjuster is to be driven as a result of checking whether the lash adjuster is to be driven.
The control method may further include determining, by the controller, whether to operate a hydraulic control mechanism when the lash adjuster does not have to be driven as a result of checking whether to drive the lash adjuster, wherein the controller may set the reference region to a first reduced oil pressure region when the oil pressure in the main line is compared with the reference region when the hydraulic control mechanism is to be operated as a result of determining whether to operate the hydraulic control mechanism; and the controller may set the reference region to a second reduced oil pressure region lower than the first reduced oil pressure region when it is not necessary to operate the hydraulic control mechanism.
According to the control system and the control method for the hydraulic variable valve having the above-described configuration, it is possible to control the engine oil pressure according to the operating conditions of the vehicle and simultaneously realize the CDA function by using the single OCV. Because of this, various functions can be performed at reduced cost, thereby achieving reduction in manufacturing cost and packaging volume.
Further, due to the adjustment of the oil pressure, the driving torque of the oil pump and the friction between engine parts can be reduced, thereby improving the fuel mileage of the engine.
Drawings
In order that the disclosure may be well understood, various forms thereof will now be described, by way of example, with reference to the accompanying drawings, in which:
FIG. 1 is a block diagram schematically illustrating a control system for a hydraulically variable valve, according to aspects of the present disclosure;
fig. 2 to 4 are views illustrating oil flow and operation according to each control mode of the control system for a hydraulic variable valve according to the present disclosure;
FIG. 5 is a table illustrating an operation table for a control system for a hydraulic variable valve according to aspects of the present disclosure; and
fig. 6 is a flowchart illustrating a control method for a hydraulic variable valve according to an aspect of the present disclosure.
The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way.
Detailed Description
The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. It should be understood that throughout the drawings, corresponding reference numerals indicate like or corresponding parts and features.
Fig. 1 is a block diagram schematically illustrating a control system for a hydraulic variable valve according to one form of the present disclosure, and fig. 2 to 4 are views illustrating oil flow and operation for each control mode of the control system for a hydraulic variable valve according to the present disclosure.
Referring to fig. 1 to 4, a control system for a hydraulic variable valve according to the present disclosure may include: an Oil Control Valve (OCV)100 configured with: a housing 110 in which a flow passage 111 is defined, a main port 113 that is provided on an outer circumferential surface of the housing 110 and allows the flow passage 111 and the oil pump 200 to communicate with each other, first and second discharge ports 117 and 119 that are provided on an outer circumferential surface of the housing 110 and allow the flow passage 111 and the lash adjuster 300 to communicate with each other, a spool 130 that is moved along the flow passage 111 by a solenoid 120 to open and close the main port 113, the control port 115, and the first and second discharge ports 117 and 119, and a relief valve 140 that is provided in the flow passage 111 at a portion where the control port 115 and the second discharge port 119 are connected to each other and allows a pressure on a control port 115 side to be maintained at a predetermined pressure; a main line 150 connecting the main port 113 and the oil pump 200 to each other; a control line 160 connecting the control port 115 and the slack adjuster 300 to each other; an orifice 170 disposed between main line 150 and control line 160; and a controller 400 that controls the OCV100 to allow at least one combination of the main port 113 and the first discharge port 117, the control port 115 and the second discharge port 119, and the main port 113 and the control port 115 to communicate with each other.
Specifically explained, the controller 400 controls the OCV100 in one of a first mode in which the control port 115 and the second discharge port 119 communicate with each other while the main port 113 and the first discharge port 117 communicate with each other, a second mode, and a third mode; in the second mode, the main port 113 and the first discharge port 117 are closed while the control port 115 and the second discharge port 119 are communicated with each other; and in the third mode, the first discharge port 117 and the second discharge port 119 are closed while the main port 113 and the control port 115 communicate with each other.
While a typical OCV includes three ports, an OCV100 according to the present disclosure includes four ports. This configuration can achieve an improvement in fuel mileage by controlling oil pressure while achieving a Cylinder Deactivation (CDA) function by operating the lash adjuster 300.
Here, the lash adjuster 300 may be configured as a hydraulically operated Hydraulic Lash Adjuster (HLA) or a mechanically operated Mechanical Lash Adjuster (MLA).
Explained specifically, as shown in fig. 2, the housing 110 of the OCV100 has a flow passage 111 defined to allow oil to flow therein, and four ports, i.e., a main port 113, a control port 115, a first discharge port 117, and a second discharge port 119, each of which extends from the flow passage 111 to allow oil to flow into and out of the same.
The main port 113 is connected with the oil pump 200 via a main line 150 to receive oil from the oil pump 200. Alternatively, the main port 113 may be connected with the oil pump 200 via a cylinder block or a cylinder head, which may be designed to vary depending on the type of vehicle or the intention of a designer.
The first and second discharge ports 117 and 119 are openings provided to adjust pressures in the main line 150 and the control line 160, respectively, and serve as paths through which oil present in the flow passage 111 is discharged to the outside.
The OCV100 has a valve core 130 disposed therein and configured to be movable to selectively open and close four ports. The spool 130 is controlled to move together with the armature 125 by the electromotive action of the solenoid 120.
As shown in fig. 1, the controller 400 controls to drive the solenoid 120 of the OCV100, thereby causing the ports of the OCV100 to selectively perform an opening/closing operation. The controller 400 can control the OCV100 in three control modes.
Specifically explaining, depending on whether the hydraulic control mechanism is operated, the controller 400 may control the OCV100 in the first mode when the oil pressure in the main line 150 is to be regulated, may control the OCV100 in the second mode when the oil pressure in the main line 150 is to be maintained at a maximum or increased pressure, and may control the OCV100 in the third mode when the lash adjuster 300 is to be driven.
Here, the hydraulic control mechanism denotes a device hydraulically controlled according to oil, such as CVVT, and the controller 400 controls the OCV100 in the first mode to form an oil pressure in the main line 150, which is controlled by the operation of the hydraulic control mechanism.
Fig. 2 shows that the OCV100 is controlled in a first mode in which the main port 113 and the first discharge port 117 communicate with each other, so that the degree of discharging oil present in the main line 150 to the first discharge port 117 is adjusted, thereby adjusting the oil pressure in the main line 150. Further, the control port 115 and the second discharge port 119 are allowed to communicate with each other with the relief valve 140 interposed therebetween, so that when the pressure in the control line 160 is equal to or greater than a predetermined pressure, the relief valve 140 is opened to cause oil to be discharged to the second discharge port 119 so as to maintain the pressure in the control line 160 at the predetermined pressure.
The relief valve 140 is configured to define a path on the flow channel 111 and to close the path with a spring and a ball. Here, when the ball is pushed by the oil pressure flowing from the control port 115 and thus the spring is compressed, the path is opened to cause the control port 115 and the second discharge port 119 to communicate with each other. This makes it possible to maintain the pressure in the control line 160 at a predetermined level.
Fig. 3 shows the OCV100 being controlled in a second mode in which the main port 113 and the first discharge port 117 are closed while the control port 115 and the second discharge port 119 are selectively communicated with each other via the relief valve 140, thereby maintaining the oil pressure in the main line 150 at an increased pressure.
Fig. 4 shows the OCV100 being controlled in a third mode in which the spool 130 moves to cause the main port 113 and the control port 115 to communicate with each other, such that the pressure in the control line 160 increases to be equal to the pressure in the main line 150. Here, since the control line 160 is connected with the slack adjuster 300, the slack adjuster 300 operates to release the latching pin, thereby implementing the CDA function.
Here, as shown in fig. 2 to 4, the slack adjuster 300 may be configured as a single type of slack adjuster that is operable only with the control line 160 connected thereto. Alternatively, the slack adjuster 300 may be configured as a dual type slack adjuster operable with the main line 150 and the control line 160 connected thereto such that operation is performed due to a pressure differential between the main line 150 and the control line 160.
When the OCV100 is controlled in the first mode, the controller 400 may control the OCV100 such that the opening degree of the first discharge port 117 is increased when the oil pressure in the main line 150 is higher than a reference region; and when the oil pressure in the main line 150 is lower than the reference region, the opening degree of the first discharge port 117 is decreased.
In other words, the opening degree of the first discharge port 117 is adjusted in a state where the OCV100 is controlled in the first mode, thereby causing a change in the oil pressure in the main line 150. Because of this, the oil pressure desired by the hydraulic control mechanism can be achieved.
If the OCV100 is controlled such that the opening degree of the first discharge port 117 increases, the amount of oil discharged from the main port 113 to the first discharge port 117 increases, thereby reducing the oil pressure. In contrast, if the OCV100 is controlled such that the opening degree of the first discharge port 117 decreases, the amount of oil discharged from the main port 113 to the first discharge port 117 decreases, thereby increasing the oil pressure.
If the oil pressure in the main line 150 is included in the reference region, the opening degree of the first discharge port 117 may be fixed to thereby form the oil pressure according to the needs of the hydraulic control mechanism. As described above, when the oil pressure in the main line 150 is controlled to be reduced, the driving torque for the oil pump 200 is caused to be reduced, thereby improving the fuel mileage of the engine.
Additionally, when the OCV100 is controlled in the first mode, the hydraulic control mechanism is operated, and the controller 400 may set the reference region to a first minimum or reduced oil pressure region. When the hydraulic control mechanism is not operated, the controller 400 may set the reference region to a second minimum or reduced oil pressure region that is lower than the first reduced oil pressure region.
In other words, the controller 400 controls the OCV100 in the first mode such that the oil pressure is included in the first reduced oil nip, which is a reduced pressure that satisfies the operating conditions of the hydraulic control mechanism. Because of this, it is possible to enable the oil pressure in the main line 150 to be maintained at a reduced level to reduce the drive torque for the oil pump 200, thereby achieving a significant reduction in engine fuel mileage.
In contrast, when the operation of the hydraulic control mechanism is not employed, the controller 400 controls the OCV100 in the first mode such that the oil pressure in the main line 150 is included in a second reduced oil pressure zone lower than the first reduced oil pressure zone, thereby reducing the oil pressure in the main line 150.
Here, the second reduced oil pressure region is set as an oil pressure region that allows the OCV100 to function well and permanently, and may be derived through a plurality of experiments.
FIG. 5 is a table showing an operating table for a control system for a hydraulically variable valve according to one form of the present invention.
Referring to fig. 5, the third mode of OCV is performed only when the CDA function is activated. On the other hand, when the CDA function is not activated, the first and second modes are selectively executed, so that the controller controls the OCV in the second mode when it is desired to maintain the oil pressure at an increased pressure, and in the first mode when it is desired to change the oil pressure, depending on whether the hydraulic control mechanism is operated. Here, the spool position and the level of the drive current will be described later.
The OCV100 is configured such that a first discharge port 117, a main port 113, a control port 115, and a second discharge port 119 are formed on the outer circumferential surface of the housing 110 to be sequentially arranged in a downward direction or a reverse direction. The spool 130 may be normally positioned at an initial point, allowing the control port 115 and the second discharge port 119 to communicate with each other via the relief valve 140, while allowing the main port 113 and the first discharge port 117 to communicate with each other.
Specifically explained, the spool 130 may have a first end coupled to the armature 125 moved by the solenoid 120 and a second end coupled to a compression spring 135 providing elasticity to the spool, whereby the spool 130 is normally positioned at an initial point.
In other words, when the spool 130 is not moved by the solenoid 120, as shown in fig. 2, the spool 130 is in close contact with the upper or lower end of the flow passage 111 defined in the housing 110 due to the elasticity of the compression spring 130 acting on the spool 130. Here, the valve body 130 is in a state of realizing the first mode of the OCV 100.
In one aspect, the initial point of the spool 130 may be determined as a position where the oil pressure is maximally reduced by maximally increasing the opening degree of the first discharge port 117. When the spool 130 is moved by the armature 125 and thus spaced apart from the initial point when the solenoid 120 operates, the opening degree of the first discharge port 117 is thereby reduced.
When the OCV100 is controlled in the first mode, the controller 400 may not drive the solenoid 120. When the OCV100 is controlled in the second mode, the controller 400 may drive the solenoid 120 by the first set value such that the spool 130 moves from the initial point to the first point. When the OCV100 is controlled in the third mode, the controller 400 may drive the solenoid 120 by a second set value greater than the first set value such that the spool 130 moves from the initial point to the second point.
In other words, in the present disclosure, the OCV100 is initially in the first mode when the controller 400 does not apply the driving current to the solenoid 120. As the driving current of the solenoid is gradually increased, the spool 130 moves and thus decreases the opening degree of the first discharge port 117. When the solenoid 120 is driven by the first set value, the first discharge port 117 is completely closed and enters the second mode. Further increasing the drive current of the solenoid decreases the opening degree of the second discharge port 119. When the drive current reaches the second set value, the main port 113 and the control port 115 are allowed to communicate with each other and enter the third mode.
As described above, the controller 400 controls the OCV100 in the order of the first mode, the second mode, and the third mode by gradually increasing the driving current.
Hereinafter, a control method for a hydraulic variable valve according to one aspect of the present disclosure will be described with reference to the accompanying drawings.
Fig. 6 is a flowchart illustrating a control method for a hydraulic variable valve according to an aspect of the present disclosure. Referring to fig. 6, a control method for a hydraulic variable valve according to the present disclosure may include: comparing, by the controller, the oil pressure in the main line with a reference zone (S30); and as a result of comparing the oil pressure in the main line with the reference zone (S30), controlling the OCVs by the controller in the first mode such that the opening degree of the first discharge port is maintained when the oil pressure in the main line is included in the reference zone, the opening degree of the first discharge port is increased when the oil pressure in the main line is lower than the reference zone, and the opening degree of the first discharge port is decreased when the oil pressure in the main line is higher than the reference zone (S40).
Further, the control method for the hydraulic variable valve may further include: before comparing the oil pressure in the main line with the reference zone (S30), it is checked by the controller whether the lash adjuster is to be driven (S10), wherein when the lash adjuster is to be driven, the controller controls the OCV in the third mode (S50) as a result of checking whether the lash adjuster is to be driven (S10).
The control method for the hydraulic variable valve may further include: determining, by the controller, whether the hydraulic control mechanism is to be operated (S20) when the lash adjuster is not to be driven (S10) as a result of checking whether the lash adjuster is to be driven (S10), wherein the controller sets a reference region as a first reduced oil pressure region when the oil pressure in the main line is compared (S30-1) with the reference region when the hydraulic control mechanism is to be operated (S20) as a result of determining whether the hydraulic control mechanism is to be operated (S30-1); and when it is not necessary to operate the hydraulic control mechanism, the controller sets the reference region to a second reduced oil pressure region lower than the first reduced oil pressure region (S30-2).
According to the control system and the control method for the hydraulic variable valve having the above-described configuration, it is possible to control the engine oil pressure according to the vehicle while implementing the CDA function using a single OCV. Because of this, various functions can be performed at reduced cost, thereby achieving reduction in manufacturing cost and packaging volume.
Further, due to the adjustment of the oil pressure, the driving torque of the oil pump and the friction between engine parts can be reduced, thereby improving the fuel mileage of the engine.
Although aspects of the present disclosure have been described for illustrative purposes, those skilled in the art will appreciate that various modifications, additions and substitutions are possible, without departing from the scope and spirit of the invention as disclosed in the accompanying claims.
Claims (18)
1. A control system for a hydraulically variable valve, the control system comprising:
an oil control valve configured with a housing defining a flow passage, a main port provided on an outer peripheral surface of the housing and making the flow passage and an oil pump communicate with each other, first and second discharge ports provided on the outer peripheral surface of the housing and making the flow passage and a lash adjuster communicate with each other, a spool moved by a solenoid along the flow passage to open and close the main port, a control port, and the first and second discharge ports, and a relief valve provided in the flow passage at a portion where the control port and the second discharge port are connected to each other and making a pressure on a control port side maintained at a predetermined pressure;
a main line connecting the main port and the oil pump to each other;
a control line connecting the control port and the slack adjuster to each other;
an orifice disposed between the main line and the control line; and
a controller that controls the oil control valve such that at least one combination of the main port and the first discharge port, the control port and the second discharge port, and the main port and the control port communicate with each other.
2. The control system of claim 1, wherein the controller controls the oil control valve in one of a first mode, a second mode, and a third mode, wherein
In the first mode, the control port and the second discharge port communicate with each other while the main port and the first discharge port communicate with each other;
in the second mode, the main port and the first discharge port are closed while the control port and the second discharge port are communicated with each other; and is
In the third mode, the first and second discharge ports are closed while the main port and the control port communicate with each other.
3. The control system according to claim 2, wherein the controller controls the oil control valve in the first mode to regulate the oil pressure in the main line, controls the oil control valve in the second mode to maintain the oil pressure in the main line at an increased pressure, and controls the oil control valve in the third mode when the lash adjuster is to be driven, depending on whether a hydraulic control mechanism is operated.
4. The control system according to claim 3, wherein when the oil control valve is controlled in the first mode, the controller controls the oil control valve such that an opening degree of the first discharge port increases when an oil pressure in the main line is higher than a reference region; and the opening degree of the first discharge port is decreased when the oil pressure in the main line is lower than the reference region.
5. The control system of claim 4, wherein when the oil control valve is controlled in the first mode, the controller sets the reference zone to a first reduced oil pressure zone when the hydraulic control mechanism is operated and sets the reference zone to a second reduced oil pressure zone when the hydraulic control mechanism is not operated, the second reduced oil pressure zone being lower than the first reduced oil pressure zone.
6. The control system according to claim 2, wherein the oil control valve is configured such that the first discharge port, the main port, the control port, and the second discharge port are formed on the outer peripheral surface of the housing so as to be arranged sequentially in a downward direction or a reverse direction, and
the spool is normally positioned at an initial point such that the control port and the second discharge port communicate with each other via the relief valve while the main port and the first discharge port communicate with each other.
7. The control system of claim 6, wherein the spool has a first end coupled to an armature moved by the solenoid and a second end coupled to a compression spring that provides resiliency to the spool, whereby the spool is normally positioned at the initial point.
8. The control system of claim 6, wherein the controller does not drive the solenoid when the oil control valve is controlled in the first mode; when controlling the oil control valve in the second mode, the controller drives the solenoid by a first set value such that the spool moves from the initial point to a first point; and when the oil control valve is controlled in the third mode, the controller drives the solenoid by a second set value that is greater than the first set value such that the spool moves from the initial point to a second point.
9. A control method for the control system according to claim 1, the control method comprising:
comparing, by the controller, the oil pressure in the main line to a reference zone; and
as a result of comparing the oil pressure in the main line with the reference region, controlling, by the controller, the oil control valve in a first mode such that an opening degree of a first discharge port is maintained when the oil pressure in the main line is included in the reference region, the opening degree of the first discharge port is increased when the oil pressure in the main line is lower than the reference region, and the opening degree of the first discharge port is decreased when the oil pressure in the main line is higher than the reference region.
10. The control method of claim 9, further comprising:
checking by the controller whether the lash adjuster is to be driven before comparing the oil pressure in the main line with the reference zone,
wherein the controller controls the oil control valve in a third mode when the lash adjuster is to be driven as a result of checking whether the lash adjuster is to be driven.
11. The control method of claim 10, further comprising:
determining, by the controller, whether to operate the hydraulic control mechanism when it is not necessary to drive the slack adjuster as a result of checking whether to drive the slack adjuster,
wherein as a result of determining whether to operate the hydraulic control mechanism, when the hydraulic control mechanism is to be operated, the controller sets the reference region as a first reduced oil pressure region when comparing the oil pressure in the main line with the reference region; and when it is not necessary to operate the hydraulic control mechanism, the controller sets the reference region to a second reduced oil pressure region lower than the first reduced oil pressure region.
12. A control system for a hydraulically variable valve, the control system comprising:
an oil control valve configured with a housing defining a flow passage, a main port provided on an outer peripheral surface of the housing and causing the flow passage and an oil pump to communicate with each other, a first discharge port and a second discharge port provided on the outer peripheral surface of the housing and causing the flow passage and a lash adjuster to communicate with each other, a spool that is moved by a solenoid along the flow passage to open and close the main port, a control port, and the first and second discharge ports, and a relief valve that is provided in the flow passage at a portion where the control port and the second discharge port are connected to each other and causes a pressure on a control port side to be maintained at a predetermined pressure;
a main line connecting the main port and the oil pump to each other;
a control line connecting the control port and the slack adjuster to each other; and
an orifice disposed between the main line and the control line;
wherein the oil control valve is operable in at least a first mode, a second mode, and a third mode;
wherein in the first mode, the control port and the second discharge port communicate with each other while the primary port and the first discharge port communicate with each other;
wherein in the second mode, the main port and the first discharge port are closed while the control port and the second discharge port are communicated with each other;
wherein in the third mode, the first and second discharge ports are closed while the main port and the control port are in communication with each other.
13. The control system of claim 12, wherein in the first mode, oil pressure in the main line is regulated depending on whether a hydraulic control mechanism is operated; in the second mode, maintaining oil pressure in the main line at an increased pressure; and in the third mode, driving the slack adjuster.
14. The control system according to claim 13, wherein in the first mode, when the oil pressure in the main line is higher than a reference region, an opening degree of the first discharge port is increased; and the opening degree of the first discharge port is decreased when the oil pressure in the main line is lower than the reference region.
15. The control system of claim 14, wherein the reference zone is set to a first reduced oil pressure zone when the hydraulic control mechanism is operated, and is set to a second reduced oil pressure zone when the hydraulic control mechanism is not operated, the second reduced oil pressure zone being lower than the first reduced oil pressure zone.
16. The control system according to claim 12, wherein the first discharge port, the main port, the control port, and the second discharge port are formed on the outer peripheral surface of the housing so as to be sequentially arranged in a downward direction or a reverse direction, and
the spool is normally positioned at an initial point such that the control port and the second discharge port communicate with each other via the relief valve while the main port and the first discharge port communicate with each other.
17. The control system of claim 16, wherein the spool has a first end coupled to an armature moved by the solenoid and a second end coupled to a compression spring that provides resiliency to the spool, whereby the spool is normally positioned at the initial point.
18. The control system of claim 16, wherein in the first mode, the solenoid is not driven; in the second mode, the solenoid is driven by a first set value such that the spool moves from the initial point to a first point; and in the third mode, the solenoid is driven by a second set value that is greater than the first set value such that the spool moves from the initial point to a second point.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201811156115.4A CN110966062B (en) | 2018-09-30 | 2018-09-30 | Control system and control method for hydraulic variable valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811156115.4A CN110966062B (en) | 2018-09-30 | 2018-09-30 | Control system and control method for hydraulic variable valve |
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| CN110966062A CN110966062A (en) | 2020-04-07 |
| CN110966062B true CN110966062B (en) | 2022-09-27 |
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| CN201811156115.4A Active CN110966062B (en) | 2018-09-30 | 2018-09-30 | Control system and control method for hydraulic variable valve |
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| US11560813B2 (en) * | 2021-03-18 | 2023-01-24 | Schaeffler Technologies AG & Co. KG | Recirculating hydraulic fluid control valve |
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| CN110966062A (en) | 2020-04-07 |
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