Patent Application
20110225968
The present invention relates to an internal combustion engine control apparatus, and particularly to an internal combustion engine control apparatus equipped with a diaphragm-type actuator.
The conventional technology for internal combustion engine control apparatuses includes an internal combustion engine control apparatus that has a variable capacity mechanism provided on a turbine side of a variable capacity turbocharger, and a diaphragm-type actuator that drives the variable capacity mechanism, for example, as disclosed in Patent Literature 1 (Japanese Patent Laid-Open No. 11-36877). The known conventional technology also includes an internal combustion engine control apparatus that is equipped with a waste gate valve that adjusts a boost pressure of an internal combustion engine, and an actuator that drives the waste gate valve, as disclosed in Patent Literature 2 (Japanese Patent Laid-Open No. 2006-274833).
Patent Literature 1: Japanese Patent Laid-Open No. 11-36877
Patent Literature 2: Japanese Patent Laid-Open No. 2006-274833
The above-described conventional technology employs a configuration that uses a diaphragm-type actuator. However, since heat generated in an internal combustion engine is liable to be transmitted to a pressure chamber of the actuator, for example, in a case where high-load operations continue for a long time, there is the risk that the gas inside the pressure chamber will be thermally expanded and the internal pressure will rise and cause damage to the diaphragm. In particular, since the actuator that drives the waste gate valve is arranged in the vicinity of an exhaust system (turbine and the like) which becomes a high temperature, the above-described problem is liable to occur.
The present invention has been made to solve the above-described problem, and an object of the present invention is to provide an internal combustion engine control apparatus that is capable of preventing damage to a diaphragm caused by a high temperature and improving the heat resistance property of the actuator.
A first aspect of the present invention is an internal combustion engine control apparatus, comprising:
a movable mechanism provided in an internal combustion engine;
a diaphragm-type actuator in which, by disposing a flexible diaphragm inside a housing, a pressure chamber is defined on at least one side of the diaphragm, wherein the actuator drives the movable mechanism by allowing the diaphragm to bend and deform in accordance with a differential pressure that is generated between one side and another side of the diaphragm;
differential pressure generating means capable of generating the differential pressure;
actuator control means that controls an operating state of the actuator by changing the differential pressure by means of the differential pressure generating means based on operating information of the internal combustion engine;
temperature acquiring means that acquires a temperature of the actuator; and
pressure release means that releases a pressure of the pressure chamber when a temperature of the actuator exceeds a predetermined pressure release temperature.
In a second aspect of the present invention, the actuator comprises a high pressure chamber and a low pressure chamber that are defined as the pressure chamber on one side and another side of the diaphragm, respectively; and
the pressure release means is configured to release pressure from either one of the high pressure chamber and the low pressure chamber to the other of the high pressure chamber and the low pressure chamber.
In a third aspect of the present invention, the internal combustion engine control apparatus comprising:
a communication portion that allows the high pressure chamber and the low pressure chamber to communicate with each other; and
a pressure release valve that is a normally-closed valve that opens and closes the communication portion, and that opens when a state of the differential pressure satisfies a predetermined valve opening condition;
wherein the pressure release means is configured so that, when a temperature of the actuator exceeds the pressure release temperature, the valve opening condition is realized by means of the differential pressure generating means and the pressure release valve is opened.
In a fourth aspect of the present invention, the pressure release valve comprises a reed valve that is provided at a position that covers the communication portion from the low pressure chamber side, and that opens when a differential pressure in a forward direction that presses the diaphragm from the high pressure chamber side becomes equal to or greater than a predetermined valve opening pressure;
when activating the actuator, the actuator control means maintains a pressure value of the differential pressure in a forward direction at a value that is less than the valve opening pressure while generating the differential pressure; and
the pressure release means is configured to increase the differential pressure in a forward direction to a pressure that is greater than or equal to the valve opening pressure.
In a fifth aspect of the present invention, the pressure release valve comprises a reed valve that is provided at a position that covers the communication portion from the high pressure chamber side, and that opens when a differential pressure in a backward direction that presses the diaphragm from the low pressure chamber side is generated;
when activating the actuator, the actuator control means causes a differential pressure in a forward direction to be generated that presses the diaphragm from the high pressure chamber side; and
the pressure release means is configured to generate the differential pressure in a backward direction.
In a sixth aspect of the present invention, the differential pressure generating means comprises:
two pressure sources that supply pressure to the high pressure chamber and the low pressure chamber, respectively; and
a pressure regulating valve that regulates a pressure that is supplied to at least one of the high pressure chamber and the low pressure chamber.
In a seventh aspect of the present invention, the internal combustion engine control apparatus further comprising drive time release inhibiting means that inhibits operation of the pressure release means when a vehicle is moving.
In an eighth aspect of the present invention, the internal combustion engine control apparatus further comprising acceleration time release inhibiting means that inhibits operation of the pressure release means at a time of acceleration of the internal combustion engine.
In a ninth aspect of the present invention, the temperature acquiring means is configured to estimate a temperature of the actuator based on
operating information of the internal combustion engine.
In a tenth aspect of the present invention, the internal combustion engine control apparatus further comprising:
a supercharger that supercharges intake air utilizing an exhaust pressure;
wherein the movable mechanism is a waste gate valve that adjusts a boost pressure produced by the supercharger.
According to the first invention, when the actuator enters an excessively high temperature state, pressure can be released from the pressure chamber by pressure release means. It is therefore possible to prevent a gas inside the pressure chamber from thermally expanding and causing damage to the diaphragm, and also to improve the heat resistance property of the actuator.
According to the second invention, when the actuator has entered an excessively high temperature state, pressure can be released between the high pressure chamber and the low pressure chamber by the pressure release means. According to this configuration, a mechanism for pressure release can be housed inside a housing that is shut off from the outside. Consequently, since it is not necessary to provide a vent hole or the like that opens to outside as in the case of a structure in which, for example, pressure is allowed to escape to outside of the housing, foreign matter such as dust and moisture can be reliably prevented from entering into the housing from outside. Accordingly, even when a mechanism for pressure release is mounted thereto, an actuator with high reliability can be realized.
According to the third invention, when the actuator has entered an excessively high temperature state, the pressure release means can easily realize a valve opening condition of a pressure release valve by changing a direction or a pressure value of a differential pressure by means of differential pressure generating means. It is thus possible to open the pressure release valve and release the pressure from the high pressure chamber towards the low pressure chamber through a communication portion.
According to the fourth invention, by using a reed valve that has a simple structure, the communication portion can be easily opened or closed by merely changing the direction of a differential pressure or a pressure value. It is thereby possible to easily realize a mechanism for pressure release without mounting a complex valve apparatus or valve control mechanism or the like in the actuator. Accordingly, the overall actuator can be made with a small size and a light weight, and assembly thereof can be performed efficiently.
According to the fifth invention, the same operational advantages as the fourth invention can be obtained by using a reed valve. Further, since the reed valve has a structure that covers the communication portion from the high pressure chamber side, in a case where the pressure of the low pressure chamber is high when the diaphragm bends and deforms, the diaphragm can be caused to deform while opening the reed valve and releasing the pressure of the low pressure chamber. Thus, the actuator can be operated at a high speed while protecting the diaphragm.
According to the sixth invention, different pressures can be supplied to the high pressure chamber and the low pressure chamber, respectively, by two pressure sources, and a differential pressure can be efficiently generated between the two chambers. Further, the direction and pressure value of the differential pressure can be accurately controlled by a pressure regulating valve.
According to the seventh invention, drive time release inhibiting means can inhibit operation of the pressure release means when the vehicle is being driven. Therefore, since the pressure release means need not be operated when an actuator cooling effect is obtained by means of a traveling wind, the operating frequency of the pressure release means that is an emergency means can be decreased as much as possible.
According to the eighth invention, acceleration time release inhibiting means can inhibit operation of the pressure release means at the time of accelerating operation of the internal combustion engine, and thus drivability can be favorably maintained.
According to the ninth invention, temperature acquiring means can estimate the temperature of the actuator based on operating information of the internal combustion engine. Consequently, since it is not necessary to use a dedicated temperature sensor or the like for the actuator, the system can be simplified and costs can be reduced.
According to the tenth invention, by using an actuator which can release pressure at the time of a high temperature even when driving a waste gate valve in the vicinity of an exhaust system that becomes a high temperature, the waste gate valve can be stably driven.
Embodiment 1 of the present invention is described hereunder while referring to
The engine 10 also includes a supercharger 20 that supercharges intake air utilizing the exhaust pressure. The supercharger 20 includes a turbine 22 that is provided in the exhaust passage 16 and a compressor 24 that is provided in the air intake passage 14. When the supercharger 20 is operating, the turbine 22 receives the exhaust pressure and rotates to drive the compressor 24. As a result, the compressor 24 compresses and supercharges the intake air. The engine 10 also includes a bypass passage 26 that is provided in the exhaust passage 16 so as to bypass the turbine 22, and a waste gate valve (WGV) 28 that regulates the amount of exhaust gas flowing through the bypass passage 26. The WGV 28 is driven via a link mechanism 32 by a valve actuator 30, and constitutes a movable mechanism of the present embodiment. Further, pressure pipes 80 and 82, a negative pressure pump 84, and a pressure regulating valve 86 and the like that are described later are mounted as a drive system of the valve actuator 30 in the engine 10.
The system of the present embodiment is equipped with a sensor system that includes sensors 34 to 44 described below, and an ECU (Electronic Control Unit) 50 that controls the operational state of the engine 10. The sensor system will be described first. A crank angle sensor 34 outputs a signal that is synchronized with rotation of the crankshaft of the engine 10. The ECU 50 can detect the number of engine rotations and the crank angle based on the signal output from the crank angle sensor 34. An airflow sensor 36 detects the intake air amount, and an intake air temperature sensor 38 detects the temperature of the intake air. A boost pressure sensor 40 detects the pressure (boost pressure) of intake air that has been supercharged by the supercharger 20. Further, an accelerator opening sensor 42 detects an operation amount of an accelerator pedal (accelerator opening) by the driver of the vehicle, and a vehicle speed sensor 44 detects the speed of the vehicle.
In addition to the aforementioned sensors 34 to 44, the sensor system includes various sensors required for control of the vehicle and engine (for example, a water temperature sensor that detects the temperature of engine cooling water, and an air-fuel ratio sensor that detects the exhaust air-fuel ratio). These sensors are connected to the input side of the ECU 50. Fuel injection valves, spark plugs, and various actuators that include the pressure regulating valve 86 as described later are connected to the output side of the ECU 50.
The ECU 50 detects operating information of the engine by means of the sensor system, and performs operational control by driving each actuator based on the detection results. More specifically, the ECU 50 detects the number of engine revolutions and the crank angle based on the output of the crank angle sensor 34, and detects the intake air amount using the airflow sensor 36. The ECU 50 also calculates the fuel injection amount based on the intake air amount and number of engine revolutions and the like, and after deciding the fuel injection timing and ignition timing and the like based on the crank angle, the ECU 50 drives the fuel injection valves and spark plugs. Based on the output of the boost pressure sensor 40 and the like, the ECU 50 controls the degree of opening of the WGV 28 by means of the pressure regulating valve 86, and executes boost pressure control that is described later. The ECU 50 is configured to execute pressure release control that is described later when the temperature of the valve actuator 30 exceeds an allowable range.
Next, the configuration of the valve actuator 30 is described. The valve actuator 30 is configured as a diaphragm-type actuator. More specifically, the valve actuator 30 is configured so that a diaphragm 62, described later, bends and deforms in accordance with a differential pressure that is generated between one side and another side of the diaphragm 62, and drives the WGV 28.
As shown in
The diaphragm 62 is formed from a flexible material such as rubber or resin, and is disposed inside the housing 60. The diaphragm 62 includes a bottomed cylindrical cup portion 62a arranged at a center part thereof, an annular thin-walled portion 62b that projects in a flange shape from the outer circumference of the cup portion 62a, and an annular fixed portion that is formed on the outer circumference of the thin-walled portion 62b. The cup portion 62a and the fixed portion 62c are formed as thick-walled portions that have a comparatively high rigidity. The fixed portion 62c is sandwiched and held by the flange portion 60c of the housing 60 across the entire circumference thereof. The thin-walled portion 62b has flexibility, and is formed as a region that can be bent and deformed.
The diaphragm 62 defines the inside of the housing 60 into a high pressure chamber 64 and a low pressure chamber 66. These two pressure chambers are disposed on one side and the other side of the diaphragm 62, and are each formed in an airtight manner. The housing 60 is provided with two connection ports 68 and 70 that connect the high pressure chamber 64 and low pressure chamber 66 to outside, respectively. When the valve actuator 30 is operating, the high pressure chamber 64 is maintained at a higher pressure than the low pressure chamber 66, and a differential pressure (hereunder, referred to as “differential pressure in the forward direction”) in a direction that presses the diaphragm 62 towards the low pressure chamber 66 from the high pressure chamber 64 is generated between these pressure chambers. As a result, the diaphragm 62 bends and deforms towards the low pressure chamber 66 upon receiving the differential pressure in the forward direction, and is displaced in the axial direction together with the drive rod 72.
The drive rod 72 is formed, for example, in the shape of a stepped rod. The proximal end side thereof is fixed to the cup portion 62a of the diaphragm 62 inside the housing 60. The distal end side of the drive rod 72 protrudes to outside from the housing main body 60a, and is connected to the WGV 28 via the link mechanism 32 shown in
Next, the configuration of a vent hole 76 and a reed valve 78 and the like that are provided in the valve actuator 30 are described with reference to
The reed valve 78 is formed, for example, by a thin plate of metal or resin or the like that has elasticity (a spring property), and the proximal end side thereof is fixed to the bottom of the cup portion 62a. The distal end side of the reed valve 78 is retained in a closed valve position illustrated by the solid line in
Next, referring again to
In contrast, the pressure pipe 82 on the low pressure side connects the low pressure chamber 66 (connection port 70) of the valve actuator 30 to the negative pressure pump 84. The negative pressure pump 84, for example, is composed of a mechanical pump that is driven by the engine 10, and constitutes a pressure source that supplies pressure (negative pressure) to the low pressure chamber 66 through the pressure pipe 82. A pressure regulating valve 86 that regulates a negative pressure supplied to the low pressure chamber 66 from the negative pressure pump 84 is provided in the pressure pipe 82.
The pressure regulating valve 86 is composed, for example, of an electromagnetic drive-type three-way valve or the like. Based on a driving signal input from the ECU 50, some or all of negative pressure that is generated with the negative pressure pump 84 is released into the atmosphere. Accordingly, the pressure of the low pressure chamber 66 changes from a negative pressure generated by the negative pressure pump 84 to a pressure that is close to atmospheric pressure in accordance with the degree of opening of the pressure regulating valve 86. More specifically, when the pressure regulating valve 86 is fully opened, negative pressure generated with the negative pressure pump 84 is supplied as it is to the low pressure chamber 66. Further, when the pressure regulating valve 86 is fully closed, atmospheric pressure is supplied to the low pressure chamber 66. Thus, the pressure regulating valve 86 generates a differential pressure between the high pressure chamber 64 and the low pressure chamber 66, and also changes the direction and pressure value of the differential pressure. In this connection, the air intake passage 14, the negative pressure pump 84, and the pressure regulating valve 86 constitute differential pressure generating means of the present embodiment.
Next, boost pressure control executed by the ECU 50 and operations of the valve actuator 30 in this control are described. In the boost pressure control, the pressure regulating valve 86 changes the differential pressure to control the operating state (that is, the degree of opening of the WGV 28) of the valve actuator 30 based on the output of the intake air temperature sensor 38 and the boost pressure sensor 40. The boost pressure can be appropriately controlled as a result.
More specifically, first, since it is not necessary to restrict the boost pressure when the temperature of the intake air or the boost pressure is sufficiently low, the valve actuator 30 is stopped and the WGV 28 is maintained in a closed state. When stopping the valve actuator 30, for example, the pressure regulating valve 86 is fully closed, the pressure of the low pressure chamber 66 is increased as far as a pressure in the vicinity of atmospheric pressure, and the differential pressure in the forward direction is decreased. Thus, a resultant force that combines the differential pressure and the spring force of the return spring 74 acts in the direction of arrow B in
Further, according to the boost pressure control, when the temperature of intake air or the boost pressure is high, the valve actuator 30 is activated and causes the WGV 28 to open. Thereby, the boost pressure is restricted, and the occurrence of knocking or an abnormal increase in the boost pressure can be prevented. When activating the valve actuator 30, the pressure regulating valve 86 is opened to a large degree to increase the negative pressure acting on the low pressure chamber 66 and generate (increase) a differential pressure in the forward direction. Thus, a resultant force that combines the differential pressure and the spring force of the return spring 74 acts in the direction of arrow A in
When actuating the valve actuator 30 in a normal state in which pressure release control is not being executed, the ECU 50 maintains the pressure value of the differential pressure at a value that is less than the valve opening pressure of the reed valve 78 while also causing the diaphragm 62 to bend and deform by means of a differential pressure in the forward direction. More specifically, the ECU 50 maintains the degree of opening of the pressure regulating valve 86 in a state in which the degree of opening is moderately reduced from a fully open state, and supplies a negative pressure (pressure close to atmospheric pressure) that is higher than the negative pressure generated at the negative pressure pump 84 to the low pressure chamber 66. Thus, the differential pressure in the forward direction can be regulated to a pressure that is less than the valve opening pressure of the reed valve 78, and the reed valve 78 can be maintained in a closed state.
In this connection, the operations of the valve actuator 30 that are described above (regarding the direction of action of a resultant force with respect to the diaphragm 62, and the behavior of the reed valve 78 and the like) can be implemented by, for example, appropriately setting the spring force of the return spring 74, the specifications of the pressure regulating valve 86, and the valve opening pressure of the reed valve 78 and the like. Furthermore, the above-described boost pressure control is merely one example that is illustrated according to the present embodiment, and the present invention is not limited thereto.
Next, pressure release control at the time of a high temperature that is executed by the ECU 50 as well as control of the valve actuator 30 during the control is described. When the valve actuator 30 (diaphragm 62) enters an excessively high temperature state, there is a risk that, for example, gas inside the high pressure chamber 64 will undergo thermal expansion and cause the internal pressure to rise, and as a result the diaphragm 62 will be damaged. Therefore, according to the pressure release control, when a temperature t of the valve actuator 30 exceeds a predetermined pressure release temperature T1, pressure is released to the low pressure chamber 66 from the high pressure chamber 64.
More specifically, when the temperature t of the valve actuator 30 exceeds the pressure release temperature T1, a valve opening condition of the reed valve 78 (that is, a state in which the differential pressure in the forward direction becomes equal to or greater than the valve opening pressure of the reed valve 78) is realized by the pressure regulating valve 86, and the reed valve 78 is caused to open. In this case, for example, the pressure regulating valve 86 is fully opened, negative pressure generated at the negative pressure pump 84 is supplied as it is to the low pressure chamber 66, and the differential pressure in the forward direction is increased to a pressure that is greater than or equal to the valve opening pressure. Thus, since the reed valve 78 opens, pressure can be released to the low pressure chamber 66 from the high pressure chamber 64 via the vent hole 76. In this connection, the pressure release temperature T1, for example, is set to the upper limit of a temperature at which the diaphragm 62 is not damaged by an increase in the pressure of the high pressure chamber 64, and is previously stored in the ECU 50.
In contrast, it is considered that even when the temperature t is a high temperature, since the valve actuator 30 is cooled by traveling wind when the vehicle is moving, the necessity to perform pressure release control is low. Therefore, according to the present embodiment a configuration is adopted that inhibits pressure release control when it is detected that the vehicle is moving based on the output of the vehicle speed sensor 44 (more specifically, when the vehicle speed is equal to or greater than a predetermined control inhibition speed V1). The control inhibition speed V1, for example, is previously set as a minimum speed at which a cooling effect is obtained by a traveling wind. According to this configuration, since it is not necessary to execute pressure release control when a cooling effect is obtained from a traveling wind, the execution frequency of pressure release control that is control in an emergency situation can be reduced as much as possible.
Further, since there are many cases in which the valve actuator 30 is actuated and boost pressure control is performed at the time of an acceleration operation, there is the risk that the boost pressure control may be hindered by executing pressure release control. Therefore, according to the present embodiment, a configuration is adopted that inhibits pressure release control when an acceleration demand is detected based on the output of the accelerator opening sensor 42 (more specifically, when the accelerator opening is greater than or equal to a predetermined control inhibition opening A1). The control inhibition opening A1 is, for example, previously set in correspondence with an acceleration level at which there is a high possibility that boost pressure control will be executed. According to this configuration, execution of pressure release control can be prevented at the time of an acceleration operation, and thus drivability can be favorably maintained.
According to the pressure release control, the temperature t of the valve actuator 30 is estimated based on the operating information of the engine 10. More specifically, for example, the output of the engine is calculated based on the intake air amount and number of engine revolutions and the like, and the temperature t is calculated by estimation based on the output. The data necessary for this estimation processing is determined by experiment and the like, and is previously stored in the ECU 50. Thus, even without using a temperature sensor or the like, the temperature t of the valve actuator 30 can be easily acquired, and simplification of the system and a reduction in costs can be achieved. A configuration may also be adopted in which a detection result for the intake air temperature, the history of the engine output, the vehicle speed, and the like are reflected in the calculation value for the temperature t. Thus, the temperature t can be accurately estimated even in a case where the outside air temperature changes or when the vehicle is stopped while the engine is at a high temperature (a so-called “dead soak”).
Specifically, first, the output of the engine is calculated based on the intake air amount and number of engine revolutions and the like, and it is determined whether or not the engine output is less than a predetermined low output determination value P1 (step 100). If the result determined in step 100 is “Yes”, for example, the estimated temperature t is reduced by 1° C. (step 102). In contrast, if the result determined in step 100 is “No”, the ECU determines whether or not the engine output is greater than a predetermined high output determination value P2 (step 104). If the result determined in step 104 is “Yes”, for example, the estimated temperature t is increased by 1° C. (step 106).
In this case, the low output determination value P1 and the high output determination value P2 are set as the minimum value and the maximum value of the engine output at which the actuator is maintained at a constant temperature, respectively, and are previously stored in the ECU 50. The temperature t of the valve actuator 30 can be estimated by the processing of steps 100 to 106. In this connection, this estimation processing is merely one example that is illustrated using the present routine, and the present invention is not limited thereto.
In the subsequent processing, the ECU determines whether or not the temperature t is greater than the aforementioned pressure release temperature T1, and whether or not the vehicle speed is less than the aforementioned control inhibition speed V1 (step 108). If the results determined in step 108 are both “Yes”, the ECU determines whether or not the accelerator opening is less than the aforementioned control inhibition opening A1 (step 110). When these three determined results (steps 108 and 110) are all “Yes”, the ECU executes the pressure release control and opens the reed valve 78 (step 112). If any of the aforementioned three results (steps 108 and 110) is “No”, there is the possibility that the temperature of the valve actuator 30 has not risen to the extent that requires pressure release control, or that the vehicle speed is great enough to generate traveling wind, or that boost pressure control is performed at acceleration. Accordingly, in this case, the ECU does not execute the pressure release control, and executes control for normal time that includes the boost pressure control (step 114).
As described in detail above, according to the present embodiment, when the valve actuator 30 has become an excessively high temperature, the differential pressure in the forward direction is increased to a pressure that is greater than the valve opening pressure by the pressure regulating valve 86, so that the reed valve 78 can be opened. As a result, pressure can be released from the high pressure chamber 64 towards the low pressure chamber 66, and it is thus possible to prevent gas inside the high pressure chamber 64 from thermally expanding and damaging the diaphragm 62. Accordingly, the heat resistance property of the valve actuator 30 can be improved, and even when driving the WGV 28 in the vicinity of the exhaust system that becomes a high temperature, the valve actuator 30 can be stably operated.
Furthermore, according to the present embodiment, since a configuration is adopted that releases pressure between the high pressure chamber 64 and the low pressure chamber 66, the vent hole 76 and reed valve 78 and the like for pressure release can be housed inside the housing 60 that is blocked off from the outside. Hence, since it is not necessary to provide a vent hole or the like that opens to outside as in the case of a structure in which, for example, pressure is allowed to escape to outside of the housing, foreign matter such as dust and moisture can be reliably prevented from entering the housing 60 from outside. Accordingly, even when a mechanism for pressure release is mounted, an actuator with high reliability can be realized.
Since a configuration is adopted in which the vent hole 76 is provided in the diaphragm 62 and is opened and closed by the reed valve 78 with a simple structure, a mechanism for pressure release can be easily realized without mounting, for example, parts that form a passage for pressure release or a complex valve apparatus or the like in the valve actuator 30. In addition, since a valve control mechanism is also unnecessary, the reed valve 78 can be easily opened by merely changing the direction or pressure value of the differential pressure. Therefore, the overall actuator can have a small size and a light weight, and assembly thereof can be performed efficiently.
According to the present embodiment, the air intake passage 14 that is a first pressure source is connected to the high pressure chamber 64, the negative pressure pump 84 that is a second pressure source is connected to the low pressure chamber 66, and negative pressure is regulated by the pressure regulating valve 86. Therefore, different pressures can be supplied to the high pressure chamber 64 and the low pressure chamber 66, respectively, and a differential pressure can be efficiently generated between the high pressure chamber 64 and the low pressure chamber 66. Further, the direction and pressure value of the differential pressure can be accurately controlled by the pressure regulating valve 86.
According to Embodiment 1, steps 100 to 106 shown in
Next, Embodiment 2 of the present invention is described referring to
First, the structure of the valve actuator 90 will be described referring to
However, as shown in
Further, the switching valve 94 can be switched to either of positions A and B shown in
Next, control of the valve actuator 90 that is performed when boost pressure control is executed is described. First, in a normal state in which the ECU 50 does not execute pressure release control, the switching valve 94 is switched to position A. Thus, the drive system of the actuator is set to the same state as in Embodiment 1. In this state, when stopping the valve actuator 90, similarly to Embodiment 1, for example, the pressure regulating valve 86 is fully opened to decrease the differential pressure in the forward direction, and the diaphragm 62 is retained at the stop position by a resultant force in the direction of arrow B shown in
Next, operations of the valve actuator 90 during pressure release control at the time of a high temperature are described. When the temperature t of the actuator exceeds the pressure release temperature T1, the ECU 50 switches the switching valve 94 to position B and sets the degree of opening of the pressure regulating valve 86 to a degree of opening that is at least not fully open (halfway open or a fully closed state). As a result, although a negative pressure of the negative pressure pump 84 is supplied as it is to the high pressure chamber 64, a pressure that is higher than the negative pressure of the pump is supplied to the low pressure chamber 66. Hence, a differential pressure in the backward direction arises between the two pressure chambers, and a valve opening condition is realized with respect to the reed valve 92. As a result, since the reed valve 92 opens, pressure can be released via the vent hole 76.
Accordingly, operational advantages that are approximately the same as in Embodiment 1 can also be obtained with the present embodiment configured in this manner. Further, since the pressure regulating valve 86 and the switching valve 94 are provided that correspond to two pressure sources constituted by the air intake passage 14 and the negative pressure pump 84, the direction and pressure value of a differential pressure can be controlled with greater efficiency.
Further, according to the present embodiment, since a configuration is adopted in which the reed valve 92 covers the vent hole 76 from the high pressure chamber 64 side, when actuating the diaphragm 62 it is possible to prevent the pressure in the low pressure chamber 66 from transiently increasing and damaging the thin-walled portion 62b of the diaphragm 62 or the like. More specifically, when the pressure in the high pressure chamber 64 is rapidly increased, in some cases an operation by the pressure regulating valve 86 that decreases the pressure in the low pressure chamber 66 does not occur quickly enough to counteract the rapid increase in pressure, and the diaphragm 62 is displaced towards the low pressure chamber 66 in a state in which the pressure in the low pressure chamber 66 is high. In this case, there is a risk that, upon receiving a high pressure from the low pressure chamber 66, the thin-walled portion 62b of the diaphragm 62 will be damaged as the result of changing shape so as to turn towards the high pressure chamber 64 side. However, when the speed of pressure increase in the high pressure chamber 64 is restricted to avoid such damage, the responsiveness of the valve actuator 90 or the WGV 28 decreases.
In contrast, according to the present embodiment, if the pressure of the low pressure chamber 66 is high when the diaphragm 62 bends and deforms, the reed valve 92 is opened by a differential pressure in the backward direction, and the pressure in the low pressure chamber 66 can be released to the high pressure chamber 64 side. More specifically, even when operating the valve actuator 90 at a high speed, the diaphragm 62 can be allowed to change shape while releasing pressure from the low pressure chamber 66, and the thin-walled portion 62b and the like can be protected from damage.
When the result determined at step 208 is “Yes”, the switching valve 94 is switched to position B and the aforementioned pressure release control is executed to open the reed valve 92 (step 210). Further, when the result determined at step 208 is “No”, the switching valve 94 is switched to position A and normal control including boost pressure control is executed (step 212).
According to Embodiment 2, steps 200 to 206 in
The foregoing embodiments describe cases which take as examples the valve actuators 30 and 90 that have the high pressure chamber 64 and the low pressure chamber 66. However, the present invention is not limited thereto. For example, the present invention may also be applied to an actuator that has only one pressure chamber and which is configured to bend and deform a diaphragm by means of a differential pressure between the pressure inside the pressure chamber and an external atmospheric pressure.
Further, according to the embodiments, the vent hole 76 is provided in the diaphragm 62 as a communication portion at which the high pressure chamber 64 and the low pressure chamber 66 communicate. However, the present invention is not limited thereto and, for example, a communication portion may be composed by a through hole that is provided at a site (for example, the drive rod 72 or the like) other than the diaphragm, or a tube or pipe or the like that is connected between the housing main body 60a and the cap 60b outside the actuator.
Further, according to the embodiments a configuration is adopted in which the vent hole 76 and the reed valve 78 or 92 are provided in the valve actuators 30 and 90, and the reed valve 78 or 92 is opened by pressure release control. However, the present invention does not necessarily require a structure such as a communication portion or a pressure release valve. More specifically, according to the present invention, a configuration may be adopted in which, without providing these structures, for example, a pressure that is supplied to a pressure chamber from a pressure source is decreased by pressure release means (pressure release control).
According to the embodiments a configuration is adopted which uses the air intake passage 14 and the mechanical negative pressure pump 84 as pressure sources. However, a pressure source of the present invention is not limited thereto and, for example, a configuration may be adopted which uses an electrically-driven pump or the exhaust passage 16 as a pressure source.
Furthermore, according to the embodiments a configuration is adopted in which the pressure supplied to the valve actuators 30 and 90 is controlled by the pressure regulating valve 86 and the switching valve 94. However, the present invention is not limited thereto and, for example, a variable type pump apparatus that allows a generated pressure to be changed by the ECU without using a pressure regulating valve or the like may be employed, and the differential pressure generating means may be constituted by the pump apparatus.
In addition, according to the embodiments a case is described in which the WGV 28 is taken as an example of a movable mechanism that is driven by the valve actuator 30 or 90. However, the present invention is not limited thereto, and the present invention is applicable to an arbitrary movable mechanism that is mounted in the internal combustion engine and driven by an actuator.
10 engine (internal combustion engine), 12 cylinder, 14 air intake passage (pressure source, differential pressure generating means), 16 exhaust passage, 18 throttle valve, 20 supercharger, 22 turbine, 24 compressor, 26 bypass passage, 28 waste gate valve (movable mechanism), 30,90 valve actuator (actuator), 32 link mechanism, 50 ECU, 60 housing, 62 diaphragm, 64 high pressure chamber (pressure chamber), 66 low pressure chamber (pressure chamber), 72 drive rod, 74 return spring, 76 vent hole (communication portion), 78 reed valve (pressure release valve), 80,82 pressure pipe, 84 negative pressure pump (pressure source, differential pressure generating means), 86 pressure regulating valve (differential pressure generating means), 94 switching valve (pressure regulating valve, differential pressure generating means), t temperature, T1 pressure release temperature
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2010/052866 | 2/24/2010 | WO | 00 | 11/29/2010 |
