Patent Application
20110253919
The present invention relates to a technology of controlling an electric current magnetizing a solenoid of an electromagnetic on/off control valve incorporated in a vehicle.
An on/off control valve (such as, for instance, a three-way valve), forming one kind of an electromagnetic directional control valve and used in a vehicular hydraulic control circuit, has flow passages switched on a flow-passage switching control. With such a flow-passage switching control, a solenoid incorporated in the on/off control valve is placed in an electrically-magnetized state i.e., excited state, or a non-electrically-magnetized state, i.e., unexcited state. This allows the flow passages of the on/off control valve to be switched in line with the respective states of the solenoid. With the solenoid remained magnetized in such a flow-passage switching control, the solenoid generates an magnetic force higher than and against an urging force of a spring or the like incorporated in the on/off control valve, thereby sustaining the flow passage in line with the electrically-magnetized state of the solenoid.
The flow-passage switching control of the related art mentioned above, has been executed using a driver circuit in which the solenoid is switched to the electrically-magnetized state or the non-electrically-magnetized state in response to a turn-on or turn-off of a given voltage of a vehicular power supply, i.e., a voltage of, for instance, a vehicular battery. That is, the solenoid is sustained in the electrically-magnetized state with a current value that is uniquely determined based on the voltage (applied voltage) applied to the solenoid, and a coil resistance of the solenoid.
The solenoid generates the magnetic force (magnetomotive force) that is determined with a product of a number of coil turns of the solenoid and the current value current-supplied to the solenoid. Thus, the higher the current value is, the higher the magnetic force (magnetomotive force) becomes. Further, the higher the coil temperature of the solenoid is, the higher the coil resistance becomes, and if the voltage applied to the solenoid is fixed, then, the current value decreases with an increase in the coil resistance. If the solenoid is current-supplied, then, the coil temperature increases. Thus, the higher the ambient temperature (such as, for instance, a temperature of hydraulic oil being supplied) of the on/off control valve is, the easier the probability of increasing the coil temperature. This causes the solenoid, remaining under a continuously current-supplied state, to have coil resistance with a coil resistance value, i.e., a saturated value being increased by such an increase in the coil temperature.
For instance, a coil-resistance increasing characteristic, shown in
Consequently, based on the coil-resistance increasing characteristic shown in
Examples of the usage condition under which the coil resistance is maximized have been supposed to include, for instance, the ambient temperature of the on-off control valve. Under a situation where the coil resistance has the maximum resistance value, more particularly, even under a condition where the coil resistance lies at a saturated resistance value at an ambient temperature (at a maximum operating temperature) under such a usage condition, an attempt has been made to design to allow the voltage of the vehicular power supply to electrically magnetize the solenoid for switching the flow passages. The flow passage witching control of the related art has been executed to current-supply the solenoid with a fixed applied voltage regardless of whether or not the coil resistance varies in a value below the saturated resistance value. That is, current-supplying the solenoid with the current value that is uniquely determined with the applied voltage and the coil resistance has resulted in placement of the solenoid in a electrically-magnetized state.
Meanwhile, a control device for controlling a drive current of a linear solenoid valve operative to adjust an output hydraulic pressure has been conventionally well known. For instance, such control device is disclosed in Patent Publication 1. The linear solenoid valve, controlled with such a control device disclosed in Patent Publication 1, has a structure to allow the linear solenoid to provide an output hydraulic pressure that varies as a parameter of the drive current. Moreover, the control device disclosed in Patent Publication 1, is arranged to perform current control so as to allow the driver current to match a drive current target value enabling the realization of a given output hydraulic target value for thereby controlling an output hydraulic pressure of the linear solenoid valve.
As set forth above, in the conventional flow passage switching control for the vehicular on/off control valve, the current value of the solenoid is uniquely determined in terms of the applied voltage and the coil resistance with no effort of positively controlling a current of the solenoid. Turning on or turning off the voltage of the vehicular power supply causes the solenoid to be switched in the electrically-magnetized state or the non-electrically-magnetized state. With the control device for the linear solenoid valve disclosed in Patent Publication 1, a current control for the drive current has been conducted for regulating the output hydraulic pressure mentioned above.
In the on/off control valve with no need to continuously vary an operating state, however, it is suffice for the solenoid to be switched to the electrically-magnetized state or the non-electrically-magnetized state in the related art. That is, it has been considered that the solenoid is suffice to be switched to a turn-on state or turn-off state with no need to control a current-supplying current (drive current) of the solenoid. In addition, the current control disclosed in Patent Publication 1 is performed with an object to controlling the output hydraulic pressure upon continuously varying the operating state of the linear solenoid valve. Thus, Patent Publication 1 was lack of motivational disclosure to anticipate such an object.
Meanwhile, though unknown, it is considered that with the flow passage switching control for the on/off control valve of the related art, if the coil resistance of the solenoid does not reach the maximum resistance value (for instance, of the saturated resistance value at the highest operating temperature), the solenoid is inevitably current-supplied with a large current beyond necessity for the purpose of sustaining the switched state (turn-on state of the on/off control valve) of the flow passage under the electrically-magnetized state of the solenoid. That is, it is considered that there is a case of causing wasteful power consumption to occur. As used herein, “the case where the coil resistance of the solenoid does not reach the maximum resistance value” may include a situation where the ambient temperature of the on/off control valve lies at, for instance, a normal temperature (of, for instance, 20° C.).
The driver circuit is designed to provide a saturated resistance value at the maximum operating temperature shown in
With the on/off control valve having a coil-resistance increasing characteristic shown in
Further, the required sustaining current value for sustaining the operating state of the on/off control valve in the turn-on state is lower than that in which the solenoid is electrically-magnetized to mechanically actuate a valve element incorporated in the on-/off control valve. Therefore, when attempting to switch the operating state of the on/off control valve from the turn-off state to the turn-on state and subsequently sustaining the turn-on state, the wasteful power consumption further increases.
The present invention has been completed with the above view in mind and has an object to provide a control device for a vehicular on/off control valve that can reduce a current value current-supplied to a solenoid of the on/off control valve to minimize power consumption of the on/off control valve.
For achieving the above object, a first aspect of the present invention provides a control device for a vehicular on/off control valve used in a hydraulic control circuit of a vehicle for switching an operating state of the on/off control valve between a turn-on sate or a turn-off state on electrically-magnetizing, i.e., exciting, or non-electrically-magnetizing, i.e., unexciting a solenoid incorporated in the on/off control valve. The control device is operable to set a current value current-supplied, i.e., driven by current to the solenoid in an operation initiating current value needed for initially switching the on/off control valve from the turn-off state to the turn-on state during an electrically-magnetized state of the solenoid, and in a sustaining current value lower than the operation initiating current value and needed for sustaining the turn-on state after switched to the turn-on state.
In a second aspect of the present invention, a feedback control is performed to match the sustaining current value with a predetermined target sustaining current value.
In a third aspect of the present invention, the current value to be current-supplied to the solenoid is set in the operation initiating current value, until a predetermined initial current-supplying time elapses from issuance of a command for switching the on/off control valve from the turn-off state to the turn-on state, and in the sustaining current value after a lapse of the initial current-supplying time.
In a fourth aspect of the present invention, the initial current-supplying time is determined based on a temperature of a hydraulic oil supplied to the on/off control valve by referring to a pre-stored relationship.
In a fifth aspect of the present invention, the initial current-supplying time is determined to be longer as temperature of the hydraulic oil becomes lower.
In a sixth aspect of the present invention, the operation initiating current value is determined based on a pressure of the hydraulic oil supplied to the on/off control valve by referring to a pre-stored relationship.
In a seventh aspect of the present invention, the on/off control valve includes an input port to which the hydraulic oil is supplied, an output port, and a valve element actuated by the solenoid, the valve element is operative to allow the input port and the output port to communicate with each other upon current-supplying of the solenoid, and to close the input port upon non-current-supplying of the solenoid, and the operation initiating current value is determined to be low as the pressure of the hydraulic oil becomes higher.
In a eighth aspect of the present invention, the on/off control valve includes an input port to which the hydraulic oil is supplied, an output port, and a valve element actuated by the solenoid, the valve element is operative to close the input port upon current-supplying of the solenoid, and to allow the input port and the output port to communicate with each other upon non-current-supplying of the solenoid, and the operation initiating current value is determined to be higher as the pressure of hydraulic oil becomes higher.
In a ninth aspect of the present invention, a feed forward control is performed in which the sustaining current value is determined based on a output voltage of a power source and the ambient temperature of the on/off control valve by referring to a pre-stored relationship decided so as to match the sustaining current value with a predetermined target sustaining current value.
According to the present invention in the first aspect, the control device is operable to set a current value current-supplied to the solenoid in an operation initiating current value needed for initially switching the on/off control valve from the turn-off state to the turn-on state during an electrically-magnetized state of the solenoid, and in a sustaining current value lower than the operation initiating current value and needed for sustaining the turn-on state after switched to the turn-on state. This reduces the current value current-supplied to the solenoid without causing any deterioration in operation of the on/off control valve. In particular, the current value can be reduced without sacrificing mechanical response of the on/off control valve. This minimizes the power consumption of the on/off control valve to be lower than that achieved in a case where no current value is switched in such a way described above. As used herein, the term “mechanical response” refers to switching response of the on/off control valve with the operating state being switched from the turn-off state to the turn-on state when the solenoid is electrically switched from a non-electrically-magnetized state to an electrically-magnetized state.
With the present invention in the second aspect, a feedback control is performed to match the sustaining current value with a predetermined target sustaining current value. This causes the current value current-supplied to the solenoid to be stably converged with the target sustaining current value, thereby reliably sustaining the turn-on state.
With the present invention in the third aspect, the current value to be current-supplied to the solenoid is set in the operation initiating current value, until a predetermined initial current-supplying time elapses from issuance of a command for switching the on/off control valve from the turn-off state to the turn-on state, and in the sustaining current value after a lapse of the initial current-supplying time. Accordingly, determining lapse of the initial current-supplying time lowers the current value from the operation initial current value to the sustain current value, so that the power consumption in the on/off control valve can be suppressed.
With the present invention in the fourth aspect, the initial current-supplying time is determined based on a temperature of a hydraulic oil supplied to the on/off control valve by referring to a pre-stored relationship. This can ensure that the on/off control valve has appropriate mechanical response while suppressing influence of an impact resulting from the temperature of hydraulic oil.
With the present invention in the fifth aspect, the initial current-supplying time is determined to be longer as temperature of the hydraulic oil becomes lower. This can avoid the temperature of hydraulic oil from giving the impact on mechanical response of the on/off control valve. This ensures stable mechanical response of the on/off control valve.
With the present invention in the sixth aspect, the operation initiating current value is determined based on a pressure of the hydraulic oil supplied to the on/off control valve by referring to a pre-stored relationship. This can ensure that the on/off control valve has appropriate mechanical response while suppressing influence of the impact resulting from the pressure of hydraulic oil.
With the present invention in the seventh aspect, the on/off control valve includes a valve element operative to allow the input port and the output port to communicate with each other upon current-supplying of the solenoid, and to close the input port upon non-current-supplying of the solenoid, and the operation initiating current value is determined to be low as the pressure of the hydraulic oil becomes higher. Thus, the pressure of hydraulic oil supplied to the input port acts on the valve element in a direction to facilitate a movement to switch the turn-off state to the turn-on state. In this connection, the operation initiating current value is determined to be lower as the pressure of hydraulic oil becomes higher. This avoids the pressure of hydraulic oil from giving the impact on mechanical response of the on/off valve in line with the structure of the on/off control valve. As a result, the on/off control valve can be ensured to have stable mechanical response.
With the present invention in the eighth aspect, the on/off control valve includes a valve element operative to close the input port upon current-supplying of the solenoid, and to allow the input port and the output port to communicate with each other upon non-current-supplying of the solenoid, and the operation initiating current value is determined to be higher as the pressure of hydraulic oil becomes higher. Thus, the pressure of hydraulic oil supplied to the input port acts on the valve element in the direction to disturb the movement to switch the turn-off state to the turn-on state. In this connection, the operation initiating current value is determined to be higher as the pressure of hydraulic oil becomes higher. This avoids the pressure of hydraulic oil from giving an impact on mechanical response of the on/off valve in line with the structure of the on/off control valve. As a result, the on/off control valve can be ensured to have stable mechanical response.
With the present invention in the ninth aspect, a feed forward control is performed in which the sustaining current value is determined based on a output voltage of a power source and the ambient temperature of the on/off control valve by referring to a pre-stored relationship decided so as to match the sustaining current value with a predetermined target sustaining current value. Thus, an electronic control device that controls the solenoid current value by using the feed forward control is constituted more simple than an electronic control device that controls the solenoid current value by using the feedback control.
Here, preferably, the target sustaining current value is determined so as to enable the turn-on state to be sustained while minimizing the sustaining current value as low as possible when the solenoid is placed in the electrically-magnetized state. More preferably, the initial current-supplying time is the time set for temporarily increasing the current value of the solenoid for the beginning of magnetizing the solenoid with a view to improving mechanical response of the on/off control valve.
Further, the temperature of hydraulic oil supplied to the on/off control valve represents one concrete example of the ambient temperature of the on/off control valve. Thus, the initial current-supplying time may be determined based on the ambient temperature of the on/off control valve by referring to the pre-stored relationship. In addition, the initial current-supplying time may be determined to be longer as the ambient temperature of the on/off control valve becomes lower.
Hereunder, various embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
The present invention is applied to an electronic control device 90 for controlling, for instance, a vehicular automatic transmission 10.
The input shaft 22 corresponds to an input member of the transmission 10 and, with the present embodiment, includes a turbine shaft of a torque converter 32 acting as a hydrodynamic power-transmitting device driven with an engine 30 acting as a drive power source for running the vehicle. The output rotation member 24, corresponding to an output of the automatic transmission 10, functions as an output gear i.e., a differential drive gear in meshing with a differential driven gear (large diameter gear) 36 of a differential gear unit 34 shown in
The automatic transmission 10 establishes gear positions depending on combinations in connecting states of either component parts of rotary elements (sun gears S1 to S3, carriers CA1 to CA3, and ring gears R1 to R3) of the first and second shifting portions 14 and 20. Thus, one of six forward-drive gear positions (forward-drive gear positions and forward-running gear positions), involving a 1st-speed shift position (1st-speed gear position) “1-st” to a 6th-speed shift position (6th-speed gear position) “6-th”, established and one reverse-drive gear position of a rear-drive shift position (rear-drive gear position and rear-drive running gear position) “R”.
As shown in
The engagement operation table, shown in
The clutches C1 and C2 and the brakes B1 to B3 (hereinafter referred to merely as a clutch C and a brake B unless otherwise specified) include hydraulic type frictional engagement devices such as multi-disc type clutches and brakes that are controllably engaged with hydraulically operated actuators. A hydraulic control circuit 100 (see
As shown in
The electronic control unit 90 is connected to these sensors and switches to receive various signals including: the accelerator's depression-stroke (accelerator-opening) Acc; the engine rotation speed NE; the intake air quantity Q; the intake air temperature TEMPA; the throttle opening θTH; the vehicle speed V; the output rotation speed NOUT; the engine cooling water temperature TEMPW; the presence or absence of braking operation; the lever position PSH of the shift lever 72; the turbine rotation speed NT (=input shaft rotation speed NIN); and the AT oil temperature TEMPOIL, etc.
Further, the electronic control unit 90 outputs engine output control command signals SE, performing output control of the engine 30, which include: a signal for driving a throttle actuator for controlling opening and closing of an electronic control valve depending on, for instance, the accelerator-opening Acc; an injection signal for controlling a quantity of fuel injected from a fuel injection device; and an ignition timing signal applied to the fuel ignition device for controlling ignition timing of the engine 30. Further, the electronic control unit 90 outputs shift control command signals SP for performing shifting control of the automatic transmission 10, i.e., for instance, signals for controlling the linear solenoid valves SLC1, SLC2, SLB1, SLB2 and SLB3 provided in the hydraulic control circuit 100 for switching the gear position of the automatic transmission 10, and a signal for driving the linear solenoid valve SLT acting as the electromagnetic solenoid valve device for controlling a line hydraulic pressure PL1.
The hydraulic control circuit 100 includes: a switching electromagnetic solenoid valve 104 operative to be turned on and off by a switching electromagnetic solenoid 102 to generate a switching signal pressure PSW; a clutch switching valve 108 operative to switch a lockup clutch 106 in a disengaging position (turn-off side position) to be placed in a disengaged state and an engaging position (turn-on side position) to be placed in an engaged state (turn-on side position) in accordance with the switching signal pressure PSW; and a slip-control solenoid valve 110 for outputting a signal pressure PSLU corresponding to a drive current supplied from the electronic control device 90.
Further, the hydraulic control circuit 100 includes: a lockup control valve 112 operative to switch an operating state of the lockup clutch 106 in a range between a slipping state and a lockup state when the clutch switching valve 108 places the lockup clutch 106 in an engaged state; an oil cooler 114 for cooling hydraulic oil; a linear solenoid valve SLB1 for feeding hydraulic oil to or discharging hydraulic oil from the friction engaging device 115 of the brake B1; an oil cooler 114 for cooling hydraulic oil; a linear solenoid valve SLB3 for feeding hydraulic oil to or discharging hydraulic oil from the friction engaging device 120 of the brake B3; and a linear solenoid valve SLC2 for feeding hydraulic oil to or discharging hydraulic oil from the friction engaging device 124 of the clutch C2.
The hydraulic control circuit 100 incorporates therein a pump 130, driven by, for instance, by the engine 30 in order to draw hydraulic oil from an oil pan (not shown) to which hydraulic oil is circulated via a strainer 128. A first regulator valve 132 of a relief type regulates a pressure of hydraulic oil, boosted by the pump 130, to a first line pressure PL1. Likewise, a second regulator valve 134 is composed of a regulator valve of a relief type and regulates the pressure of hydraulic oil flown out of the first regulator valve 132 to generate a second line pressure PL2. A third regulator valve 136, composed of a pressure reduction valve applied with the first line pressure PL1 as an original pressure, generates a modulator pressure PM that is a predetermined fixed pressure. In addition, the first and second regulator valves 132 and 234 are applied with signal pressures delivered from linear solenoid valves (not shown) to regulate the line pressures at levels suited for the vehicle to run based on the accelerator-opening or the engine rotation speed of the engine 30, etc.
The lockup clutch 106 is a hydraulic friction clutch arranged to be brought into frictional engagement with a front cover 146 in response to a differential pressure ΔP (=PON-POFF) between an oil-chamber pressure PON applied to an engaging oil chamber 140 via an engaging oil passage 138, and a hydraulic pressure POFF applied to a disengaging oil chamber 144 via an disengaging oil chamber 144 via a disengaging oil passage 142. The torque converter 32 has operating conditions broadly classified into, for instance, a so-called unlock state with the lockup clutch 106 being unlocked in response to the differential pressure ΔP placed to be negative, a so-called slipping state with the lockup clutch 106 being half engaged in response to the differential pressure ΔP placed to be more than zero; and a so-called lockup on state with the lockup clutch 106 being completely locked in response to the differential pressure ΔP placed to be maximized. During the slipping state of the lockup clutch 106, further, zeroing the differential pressure ΔP results in a reduction in torque share of the lockup clutch 106 such that the torque converter 32 is placed in an operating state equivalent to the unlock state.
The clutch switching valve 108, operative to switch the lockup clutch 106 in an engaged state and a disengaged state, includes a spool valve element 148 for switching connecting states. In
The clutch switching valve 108 further includes: a relief port 160 to which hydraulic oil, flowed from the second regulator valve 134, is supplied; a signal pressure input port 162 to which the signal pressure PSLU is applied from the throttle control solenoid valve 110; a first signal pressure output port 163 operative to allow the signal pressure PSLU to be output from the signal pressure input port 162 during the engaging operation of the lockup clutch 106; a second signal pressure output port 164 to which a signal pressure PSLU from the signal pressure input port 162 during the releasing i.e., disengaging operation of the lockup clutch 106 is outputted; a spring 168 for urging the spool valve element 148 toward the turn-off position; and an oil chamber 170 operative to allow a switching signal pressure PSW, applied from the switching electromagnetic solenoid valve 104, to act on the spool valve element 148.
The lockup control valve 112 includes: a spool valve element 172; a spring 174 giving a thrust force to urge the spool valve element 172 toward a slip-side (SLIP) position; an oil chamber 176 applied with an hydraulic pressure PON from the engaging oil chamber 140 of the torque converter 32 for urging the spool valve element 172 toward the slip position; an oil chamber 178 applied with an hydraulic pressure POFF from the disengaging oil chamber 144 of the torque converter 32 for urging the spool valve element 172 toward a completely engaged (ON) position; an oil chamber 180 applied with the signal pressure PSLU output from the first signal pressure output port 163 of the clutch switching valve 108; and an input port 182 applied with the second line pressure PL2 regulated by the second regulator valve 134. In
The slip control valve 110 outputs the signal pressure PSLU for controlling an engaging pressure of the lockup clutch 106 during the engaging operation of the lockup clutch 106. Further, the slip control valve 110 supplies hydraulic oil to drain circuits of the linear solenoid valve SLB1, the linear solenoid valve SLB3 and the linear solenoid valve SLC2. The slip control valve 110 is a valve, to which the fixed modulator pressure PM regulated by the third regulator valve 136 is applied, which reduces the fixed modulator pressure PM to output the signal pressure PSLU, which is generated in proportion to the drive current applied form the electronic control device 90. Furthermore, the slip control valve 110 has a drain port 183 held in fluid communication with a check ball 185. Thus, the drain port 183 is shut off with the check ball 185 at all times and opened in response to a pressure applied to the check ball 185 at a level exceeding a given level for thereby discharging hydraulic oil.
The switching electromagnetic solenoid valve 104 has an input port 250 to which the modulator pressure PM is supplied, an output port 252 connected to the oil chamber 170 of the clutch switching valve 108, and a discharge port 254 through which hydraulic oil is discharged. The switching electromagnetic solenoid valve 104 allows the switching signal pressure PSW to be a drain pressure under a non-electrically-magnetized state (turn-off state). Under an electrically-magnetized state (turn-on state), the switching signal pressure PSW is caused to be the modulator pressure PM, which acts on the oil chamber 170 to move the spool valve element 148 of the clutch switching valve 108 toward the turn-on position (ON) under the engaged state. In addition, the switching electromagnetic solenoid valve 104 corresponds to an on/off control valve of the present invention. Moreover, the structure of the switching electromagnetic solenoid valve 104 will be described below in detail with reference to
The linear solenoid valve SLB1 is a regulator valve for supplying hydraulic oil to or discharging the same from the friction engaging device 116 forming the brake B1. The linear solenoid valve SLB1 has an input port 186 to which the first line pressure PL1 is applied, an output port 188 from which a hydraulic pressure is output to the friction engaging device 116, and a drain port 190 from which hydraulic oil is discharged. With the linear solenoid valve SLB1 electrically-magnetized or non-electrically-magnetized with the electronic control device 90, the linear solenoid valve SLB1 controllably regulates the first line pressure PL1 regulated with the first regulator valve 132 as the original pressure. A drain circuit 194 communicates with the drain port 190, serving as a starting point, and further communicates with an oil pan (not shown) via a check ball 192, which blocks the drain circuit 194 at all times. Upon receipt of a hydraulic pressure beyond a given pressure level, the check ball 192 is opened to discharge hydraulic oil. Further, the drain circuit 194 is connected to a first branch oil passage 198, bifurcated from a hydraulic oil supply passage 196 communicating with a second signal pressure output port 164 of the clutch switching valve 108, which has an orifice 200. The check ball 192 has an upstream side to which the slip-control solenoid valve 110 is connected via the clutch switching valve 108 and the orifice 200.
The linear solenoid valve SLB3, serving as a regulator valve for supplying hydraulic oil to and discharging the same from the frictional engaging device 120 forming the brake B3, has an input port 202 to which the first line pressure PL1 is applied, an output port 204 from which a hydraulic pressure is output to the friction engaging device 120, and a drain port 206 through which hydraulic oil is discharged. With the linear solenoid valve SLB3 electrically-magnetized or non-electrically-magnetized with the electronic control device 90, the linear solenoid valve SLB3 controllably regulates the first line pressure PL1 regulated with the first regulator valve 132 as the original pressure. A drain circuit 210 communicates with the drain port 206, serving as a starting point, and further communicates with the oil pan (not shown) via a check ball 208, which blocks the drain circuit 210 at all times. Upon receipt of the hydraulic pressure beyond a given pressure level, the check ball 208 is opened to discharge hydraulic oil.
Further, the drain circuit 210 is connected to a second branch oil passage 212, bifurcated from the hydraulic oil supply passage 196 communicating with the second signal pressure output port 164 of the clutch switching valve 108, which has an orifice 214. The check ball 208 has an upstream side to which the slip-control solenoid valve 110 is connected via the clutch switching valve 108 and the orifice 214.
The linear solenoid valve SLC2, serving as a regulator valve for supplying hydraulic oil to and discharging the same from the frictional engaging device 124 forming the clutch C2, has an input port 216 to which the first line pressure PL1 is applied, an output port 218 from which a hydraulic pressure is output to the friction engaging device 124, and a drain port 220 from which hydraulic oil is discharged. With the linear solenoid valve SLC2 electrically-magnetized or non-electrically-magnetized with the electronic control device 90, the linear solenoid valve SLC2 controllably regulates the first line pressure PL1 regulated with the first regulator valve 132 as the original pressure. A drain circuit 224 communicates with the drain port 220, serving as a starting point, and further communicates with the oil pan (not shown) via a check ball 222. Upon receipt of the hydraulic pressure beyond a given pressure level, the check ball 222 is opened to discharge hydraulic oil. Further, the drain circuit 224 is connected to a third branch oil passage 226, bifurcated from the hydraulic oil supply passage 196 communicating with the second signal pressure output port 164 of the clutch switching valve 108, which has an orifice 228. The check ball 222 has an upstream side to which the slip-control solenoid valve 110 is connected via the clutch switching valve 108 and the orifice 228.
With the hydraulic control circuit 100 of such a structure, supply states of hydraulic oil to the engaging oil chamber 140 and the disengaging oil chamber 144 are switched to switch an operating state of the lockup clutch 106 or hydraulic oil is supplied to the brakes B1 and B2 and the clutch C2 for controlling engaging pressures of these component parts.
First, description will be provided of a case in which the lockup clutch 106 is placed in a slipping state and a lockup on state. Upon operation of the switching electromagnetic solenoid valve 104, the switching signal pressure PSW is supplied to the oil chamber 170 of the clutch switching valve 108. This urges the spool valve element 148, which is consequently moved toward a turn-on position. Then, the second line pressure PL2, supplied to the input port 154, is admitted from the engaging port 152 to pass to the engaging oil passage 138 to be supplied to the engaging oil chamber 140. The second line pressure PL2, supplied to the engaging oil chamber 140, serves as a hydraulic pressure PON. At the same time, the disengaging oil chamber 144 is brought into communication with a control port 230 of the lockup control valve 112 through the disengaging oil passage 142 and the disengaging port 150 communicating with the circumventing port 158. This allows the lockup control valve 112 to regulate the hydraulic pressure POFF in the disengaging oil chamber 144. That is, the lockup control valve 112 regulates the differential pressure ΔP, i.e., the engaging pressure to cause the operating state of the lockup clutch 106 to be switched in a range from the slipping state to the lockup on state.
More particularly, when the spool valve element 148 of the clutch switching valve 108 is urged toward the engaging (ON) position, i.e., when the lockup clutch 106 is switched to the engaged state, the lockup control valve 112 prevents the signal pressure PSLU, for urging the spool valve element 172 to the completely engaged (ON) position, from being supplied to the oil chamber 180. This allows a thrust force of the spring 174 to move the spool valve element 172 toward the slipping (SLIP) position, in which the second line pressure PL2, supplied to the input port 182, is admitted from the control 230 to the circumventing port 158 to pass from the disengaging port 150 to the disengaging oil passage 142 to be supplied to the disengaging oil chamber 144. Under such a state, the differential pressure ΔP is controlled in response to the signal pressure PSLU for thereby controlling the slipping state of the lockup clutch 106. In addition, the clutch switching valve 108 allows the signal pressure input port 162 and the first signal pressure output port 163 to be brought into communication with each other only when the spool valve element 148 is urged toward the engaging (ON) position. Thus, the slip-control solenoid valve 110 can supply the signal pressure PSLU to the oil chamber 180 of the lockup control valve 112.
With the spool valve element 148 of the clutch control valve 108 urged toward the ON-position, further, the signal pressure PSLU is supplied to the oil chamber 180 for urging the spool valve element 172 toward a completely engaged (ON) position and the lockup control valve 112 operates as described below. That is, no line pressure PL2 is supplied from the input port 182 to the disengaging oil chamber 144 and hydraulic oil is discharged from the disengaging oil chamber 144 via the drain port. This allows the differential pressure ΔP to be maximized such that the lockup clutch 106 is brought into a completely engaged state.
With the lockup clutch 106 placed in the slipping state or the completely engaged state, furthermore, the clutch switching valve 108 assumes the ON-position to cause the relief port 160 and the discharge port 156 to be brought into communication with each other. This allows hydraulic oil, flown out of the second regulator valve 134, to be supplied to the oil cooler 114 via the discharge port 156.
Meanwhile, with no switching signal pressure PSW supplied to the oil chamber 170, the spool valve element 148 is toward the OFF-position due to an urging force of the spring 168. Then, the clutch switching valve 108 allows the second line pressure PL2, supplied to the input port 154, to pass from the disengaging port 150 into the disengaging oil passage 142 to be supplied into the disengaging oil chamber 144. Subsequently, hydraulic oil, discharged from the engaging oil chamber 140 to pass through the engaging oil passage 138 to the engaging port 152, is fed from the discharge port 156 to the oil cooler 114 for cooling.
With the clutch switching valve 108 placed in the OFF-position, moreover, the signal pressure input port 162, to which the signal pressure PSLU is output from the slip-control solenoid valve 110, and the second signal pressure output port 164 are brought into communication with each other. The second signal pressure output port 164 is connected to the hydraulic oil supply passage 196, as set forth above, through which hydraulic oil delivered from the slip-control solenoid valve 110 can be supplied to the first, second and third branch oil passages 198, 212 and 226.
The structure of the switching electromagnetic solenoid valve 104, corresponding to the on/off control valve of the present invention, will be described below in detail.
More particularly, the switching electromagnetic solenoid valve 104 includes: a main body member 258 made of non-magnetic material formed with the input port 250, the output port 252, the discharge port 254 and a valve chamber 256 connected to the various ports 250, 252 and 254; a spherical valve element 262 accommodated in the valve chamber 256 and having a diameter greater than an input-port-side opening aperture 260 and a discharge-port-side opening aperture 261; a plunger 264; a spring 266; and the switching electromagnetic solenoid 102, all of which have the same axes as the center axis of the input port 250. The switching electromagnetic solenoid 102 is comprised of a core 268, a cylindrical coil 270 and a bottomed cylindrical yoke 272, all of which have the same axes as the center axis mentioned above, and a magnetic body lid 274 fixedly secured to an end of the main body member 258 in opposition to the input port 256. The input port 250, the spherical valve element 262, the plunger 264, the spring 266 and the core 268 are placed in such an order along the center axis of the input port 250. In the valve chamber 256, the input-port-side opening aperture 260 and the discharge-port-side opening aperture 261 are placed in opposition to each other along the above-described center axis with the spherical valve element 262 being sandwiched therebetween.
With the yoke 272 having an open end portion plugged with the magnetic body lid 274 which is fixedly secured to the open end portion of the yoke 272, the yoke 272 and the magnetic body lid 274 constitute a housing body of the switching electromagnetic solenoid 102, within which the coil 270 and the core 268 are fixedly secured to the yoke 272. The plunger 264 has one end facing the spherical valve element 262 and the other end facing the core 268 in an area inside the coil 270. The plunger 264 is urged toward the input port 250 along the above-mentioned center axis by the spring 266 disposed between the plunger 264 and the core 268.
With the switching electromagnetic solenoid 102 (coil 270) remained under a non-electrically-magnetized state, the switching electromagnetic solenoid valve 104 has an operating state (mechanically operating state) placed under a turn-off state corresponding to the non-electrically-magnetized state.
On the contrary, with the switching electromagnetic solenoid 102 (coil 270) operated under an electrically-magnetized state, the operating state of the switching electromagnetic solenoid valve 104 is placed under the turn-on state corresponding to the electrically-magnetized state. With the switching electromagnetic solenoid valve 104 operated under the turn-on state, the plunger 264 is attracted toward the core 268 due to a magnetic force generated by the coil 270 acting against and higher than that of the urging force of the spring 266. Thus, the spherical valve element 262 blocks the discharge-port-side opening aperture 261. Then, the modulator pressure PM is admitted to the input port 250 to cause the spherical valve element 262 to be pressed against the discharge-port-side opening aperture 261 due to the modulator pressure PM to block the discharge-port-side opening aperture 261. At the same time, the input port 250 and the output port 252 are brought into communication with each other to allow the switching signal pressure PSW in the output port 252 to be the modulator pressure PM.
Thus, the switching electromagnetic solenoid valve 104 takes the form of a structure wherein the spherical valve element 262, actuated with the switching electromagnetic solenoid 102, allows the input port 250 and the output port 252 to communicate with each other on current-supplying the switching electromagnetic solenoid 102 whereas non-current-supplying the switching electromagnetic solenoid 102 causes the spherical valve element 262 to block the input port 250. In addition, the switching electromagnetic solenoid 102 corresponds to a solenoid of the present invention. With the present embodiment, moreover, although the spherical valve element 262 corresponds to a valve element of the present invention, the spherical valve element 262 and the plunger 264 may a structure composed of a unitary member. In this case, such a unitary member corresponds to the valve element of the present invention.
Although the switching electromagnetic solenoid valve 104 is composed of the three-way valve of the normally closed type, a three-way valve of a normally open type operative in a way opposite to the three-way valve of the normally closed type has been well known.
The switching electromagnetic solenoid 298 includes a core 320 through which the small diameter portion of the plunger 314 extends and which has a toric surface 318 facing one end face 316 of the large diameter portion of the plunger 314, a cylindrical coil 322 through which the large diameter portion of the plunger 314 extends, and a bottomed cylindrical yoke 324. The input port 250, the spherical valve element 310 and the plunger 314 are placed in such an order along the center axis of the input port 250. Within the valve chamber 300, an input-port-side opening aperture 306 and a discharge-port-side opening aperture 308 are placed in opposition to each other along the above-described center axis with the spherical valve element 310 being sandwiched within the valve chamber 256.
With the yoke 324 having an open end portion fixedly secured to the main body member 304 at one end in opposition to the input port 250, the yoke 324 and the main body member 304 constitute a housing body of the switching electromagnetic solenoid 298, within which the coil 322 and the core 320 are fixedly secured to the yoke 324. The plunger 314 has one end facing the spherical valve element 310 and the other end facing a stopper surface 326 formed on the yoke 324 at an inward area thereof.
With the switching electromagnetic solenoid 298 (coil 322) placed under a non-electrically-magnetized state, an operating state (mechanically operating state) of the switching electromagnetic solenoid valve 296 is placed under a turn-off state corresponding to a non-electrically-magnetized state.
On the contrary, with the switching electromagnetic solenoid 298 (coil 322) placed under an electrically-magnetized state, the operating state of the switching electromagnetic solenoid valve 296 is placed under a turn-on state corresponding to an electrically-magnetized state. With the switching electromagnetic solenoid valve 296 placed under the turn-on state, more particularly, the coil 322 generates a magnetic force with a magnitude greater than the urging force of the spring 312 and acting on the plunger 314 in a direction opposite to the urging force, causing the one end face 316 of the plunger 314 to be attracted toward the toric surface 318 of the core 320. This causes the spherical valve element 252 to block the input-port-side opening aperture 306. At the same time, the output port 252 and the discharge port 254 are brought into communication with each other to cause the switching signal pressure PSW of the output port 252 to be a drain pressure.
Thus, the switching electromagnetic solenoid valve 296 is an on/off control valve having a structure in which the spherical valve element 310, actuated with the switching electromagnetic solenoid 298, blocks the input port 250 on current-supplying the switching electromagnetic solenoid 298 whereas on non-current-supplying the switching electromagnetic solenoid 298, the input port 250 and the output port 252 are brought into communication with each other. Like the switching electromagnetic solenoid valve 104, the switching electromagnetic solenoid 298 of the switching electromagnetic solenoid valve 296 corresponds to the solenoid of the present invention. Although the spherical valve element 310 corresponds to the valve element of the present invention, the spherical valve element 310 and the plunger 314 may take the form of a structure formed in a unitary member. In this case, such a unitary member corresponds to the valve element of the present invention. To describe for a confirmatory purpose, moreover, the hydraulic control circuit 100, shown in
The electronic control device 90 electrically-magnetizes or does not electrically-magnetizes the switching electromagnetic solenoid 102, incorporated in the switching electromagnetic solenoid valve 104 used in the hydraulic control circuit 100 (see
As shown in
The electromagnetic valve driver circuit 350 includes a current controller 356 connected in series between one terminal of the switching electromagnetic solenoid 102 and a positive terminal of the battery 352, and a current detector 358 connected in series between the other terminal of the switching electromagnetic solenoid 102 and the negative terminal, i.e., the vehicle body 354, of the battery 352.
The current detector 358 includes a current detecting element 360 connected in series between the other terminal of the switching electromagnetic solenoid 102 and the vehicle body 354 for detecting the current value IRL (hereinafter referred to as “solenoid current value IRL”) current-supplied to the switching electromagnetic solenoid 102 to output a detected current signal SIRL, representing the solenoid current value IRL, to the electronic control device 90.
The current detector 360 is, for instance, a current detecting resistor element, having resistance in the order of approximately 0.5Ω, which is connected between the other terminal of the switching electromagnetic solenoid 102 and the vehicle body 354 in series. The current detector 358 detects a voltage potential ERL occurring across between both terminals of the current detecting element (resistor element) 360 to allow the calculation of the solenoid current value IRL based on the detected voltage potential ERL and a resistance value of the resistor element (current detecting element) 360.
The current controller 356 includes a current control element 362, connected between one terminal of the switching electromagnetic solenoid 102 and the positive terminal of the battery 352 in series, and a current control circuit 364 for controlling the current control element 362. With the current controller 356 controlled based on the current control signal SIC delivered from the electronic control device 90, the current control signal SIC is altered. Upon receipt of the current control signal SIC representing a current value of 0 (zero), the current controller 356 allows the current control element 362 to interrupt the current-supplying of the switching electromagnetic solenoid 102.
The current control element 362 is, for instance, a PNP transistor having an emitter terminal connected to the positive terminal of the battery 352 and a collector terminal connected to one terminal of the switching electromagnetic solenoid 102. The current controller 356 sets the control current value ICON (base current value) for the current control element 362 using the current control circuit 364 to regulate the solenoid current value IRL.
The electronic control device 90 of the present embodiment controls the solenoid current value IRL and, to this end, includes solenoid electric-magnetization determining portion or means 380, operating-state switching-time determining portion or means 384 and current control portion or means 386 shown in
The solenoid electric-magnetization determining means 380 makes a query as to whether a solenoid electrically-magnetizing command is made to magnetize the switching electromagnetic solenoid 102 for the purpose of switching the operating state of the switching electromagnetic solenoid valve 104 from the turn-off state to the turn-on state. The solenoid electrically-magnetizing command is made, for instance, when attempting the switching signal PSW to be se to the modulator pressure PM, and cancelled when attempting the switching signal PSW to be set to the drain pressure PSW.
The operating-state switching-time determining means 384 makes a query as to whether a given initial current-supplying time TINT has elapsed from the issuance of a switching command to shift from the turn-off state to the turn-on state, i.e., a time (at which the solenoid electrically-magnetizing command is initiated) when the solenoid electrically-magnetizing command is initiated.
Here, the operating-state switching-time determining means 384 makes a query as to whether the initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command. However, a query may be made as to whether the initial current-supplying time TINT has elapsed from a time when the switching is made from the non-electrically-magnetized state to the electrically-magnetized state in response to the solenoid electrically-magnetizing command, i.e., a time at which the switching electromagnetic solenoid 102 is commenced to turn on.
Further, the “initial current-supplying time TINT” is a time set on experimental tests for temporarily increasing the solenoid current value IRL when beginning to magnetize the switching electromagnetic solenoid 102, i.e., when performing the switching operation from the turn-off state to the turn-on state. The term “mechanical response” of the switching electromagnetic solenoid valve 104 refers to switching response for the operating state of the switching electromagnetic solenoid valve 104 to be switched from the turn-off state to the turn-on state, when the switching electromagnetic solenoid 102 is electrically switched from the non-electrically-magnetized state to the electrically-magnetized state. The initial current-supplying time TINT is determined by the current control means 386. Accordingly, prior to making a query as to whether there is an elapse of the initial current-supplying time TINT, the operating-state switching-time determining means 384 reads out the determined initial current-supplying time TINT. After the readout has been completed, a query is made as to whether the initial current-supplying time TINT has elapsed. Detailed description will be provided of how the initial current-supplying time TINT is determined.
The current control means 386 selectively switches the switching electromagnetic solenoid 102 in one of the electrically-magnetized state and the non-electrically-magnetized state. That is, when the solenoid electric-magnetization determining means 380 determines that no solenoid electrically-magnetizing command is generated, the current control signal SIC, representing a zeroed solenoid current value IRL, is output to the current control means 386. This causes the current control element 362 to interrupt the current-supplying of the switching electromagnetic solenoid 102, which is consequently placed in the non-electrically-magnetized state. On the contrary, if the solenoid electric-magnetization determining means 380 determines that the solenoid electrically-magnetizing command is initiated, the current control means 386 allows the current controller 356 to begin current-supplying the switching electromagnetic solenoid 102, which is consequently placed in the electrically-magnetized state.
Further, under a circumstance where the switching electromagnetic solenoid 102 is placed in the electrically-magnetized state, the current control means 386 allows the solenoid current value IRL to be set to an operation initiating current value IRN required for the turn-off state to be switched to the turn-on state at the beginning of magnetization. After the switching made to the turn-on state, a solenoid control is executed with a sustaining current vale IHD lower than the operation initiating current value IRN required for sustaining the turn-on state. To describe for confirmatory purpose, all of the solenoid current value IRL, the operation initiating current value IRN and the sustaining current vale IHD represent actual current values current-supplying to the switching electromagnetic solenoid 102. That is, the operation initiating current value IRN means the solenoid current value IRN at the beginning of the magnetization and the sustaining current vale IHD means the solenoid current value IRL appearing after the switching is made to the turn-on state.
The solenoid control will be described below in detail. When the solenoid electric-magnetization determining means 380 determines that the solenoid electrically-magnetizing command is generated and the operating-state switching-time determining means 384 determines that no given initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command, the current control means 386 sets the solenoid current value IRL to be the operation initiating current value IRN. In brief, a phase in which the initial current-supplying time TINT elapses from the issuance of the solenoid electrically-magnetizing command corresponds to the beginning of magnetization. Upon receipt of the solenoid electrically-magnetizing command, the current control means 386 executes a solenoid initial-operation control in response to the solenoid current value IRL in line with the operation initiating current value IRN until the initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command. More particularly, during the solenoid initial-operation control, the current control means 386 outputs the current control signal SIC, corresponding to a predetermined target operation initiating current value ITRN, to the current controller 356. This allows the current controller 356 to set the control current value ICON at a level depending on the current control signal SIC, thereby permitting the operation initiating current value IRN (solenoid current value IRL) to be controlled so as to reach the target operation initiating current value ITRN.
When the solenoid electric-magnetization determining means 380 determines that the solenoid electrically-magnetizing command is generated and the operating-state switching-time determining means 384 determines that the given initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command, the current control means 386 executes a solenoid sustaining current control in response to the solenoid current value IRL in line with the sustaining current value IHD. In brief, when the solenoid electrically-magnetizing command is generated, if the initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command, the current control means 386 executes the solenoid sustaining current control. In such a way, the current control means 386 executes the solenoid control in which the solenoid initial-operation control is initiated before an elapse of the initial current-supplying time TINT whereas executing the solenoid sustaining current control after the elapse of the initial current-supplying time TINT.
The current control means 386 executes the solenoid sustaining current control in such a fashion described above. In such a case, a feedback control is performed to allow the sustaining current value IHD (solenoid current value IRL) to approach the predetermined target operation initiating current value ITRN, thereby executing the solenoid sustaining current control. More particularly, the feedback control is performed so as to regulate the control current value ICON of the current control element 362 such that the sustaining current value IHD lies at the predetermined target operation initiating current value ITRN. To this end, the current control means 386 executes the feedback control in a manner described below.
First, the current control means 386 reads the sustaining current value IHD when supplied with the solenoid current value IRL from the current detector 358. Then, the current control means 386 calculates a control current correcting value ΔICON using a formula expressed below. Next, the current control means 386 adds the control current correcting value ΔICON, determined in a preceding setting during the feedback control, to the control current value ICON to re-determine the same, thereby updating the control current value ICON. Subsequently, the current control means 386 outputs the current control signal SIC to the current controller 356, which in turn is caused to execute the operation to current-supply the switching electromagnetic solenoid 102 with the updated current control signal SIC. The current control means 386 performs the feedback control in such a way. Further, although the control current value ICON may have a zeroed initial value, i.e., preferably, the initial value of the control current value ICON may be determined on experimental tests conducted to minimize the control current correcting value ΔICON from the initiation of the feedback control and later.
ΔICON=KP×(ITHD−IHD)+KI×∫(ITHD−IHD)×dt (1)
Further, the formula (1) above described, represents a feedback control formula having a right-hand side with a first term representing a proportional term and a second term representing an integral term. “KP” in the above formula (1) represents a proportional gain and “KI” represents an integral gain. In the above formula (1), the proportional gain KP and the integral gain KI are pre-determined on experimental tests such that a deviation e(=ITHD−IHD) is stably converged on an earlier stage.
The target sustaining current value ITHD is a target current value for the sustaining current value IHD pre-determined on experimental tests under a situation where the switching electromagnetic solenoid 102 remains in the electrically-magnetized state. It is determined such that the switching electromagnetic solenoid 102 can be maintained in the turn-on state, and the sustaining current value IHD can be decreased as quickly as possible for reducing power consumption arising when magnetizing the switching electromagnetic solenoid 102.
Further, the target operation initiating current value ITRN, representing a target current value for the operation initiating current value IRN higher than the target sustaining current value ITHD, is a target current value, determined on experimental tests. It is required for switching the operating state of the switching electromagnetic solenoid valve 104 from the turn-off state to the turn-on. For the purpose of improving mechanical response of the switching electromagnetic solenoid valve 104, the target operation initiating current value ITRN is set or determined based on a switching response characteristic of the switching electromagnetic solenoid valve 104. Such a routine will be described below.
The term “switching response characteristic” of the switching electromagnetic solenoid valve 104 represents the relationship between the mechanical response of the switching electromagnetic solenoid valve 104 and a response impact factor causing the response to vary. The response impact factor may include, for instance, the modulator pressure PM (hereinafter referred to as “supply pressure PM”) representing a pressure of hydraulic oil supplied to the switching electromagnetic solenoid valve 104, a structure of the switching electromagnetic solenoid valve 104, and an ambient temperature of the switching electromagnetic solenoid valve 104, etc. The ambient temperature of the switching electromagnetic solenoid valve 104 may be exemplified as a temperature (AT oil temperature TEMPOIL) of fluid supplied to the switching electromagnetic solenoid valve 104 and an external temperature in the vicinity of the switching electromagnetic solenoid valve 104, etc.
At the timing tA1 in
With the solenoid control of the present embodiment, on the contrary, the current control means 386 executes the solenoid initial-operation control for a time period until the initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command (at time tA1), i.e., a time interval between times tA1 and tA2. Accordingly, at time tA1, the solenoid current value IRL rises up to the target operation initiating current value ITRN. During a time period between the times tA1 and tA2, the solenoid current value IRL is maintained at the target operation initiating current value ITRN. That is, the solenoid current value IRL continuously remains constant between the times tA1 and tA2.
Next at time tA2, the operating-state switching-time determining means 384 determines that the initial current-supplying time TINT has elapsed, and the current control means 386 executes the solenoid sustaining current control. Accordingly, the solenoid current value IRL drops to the target sustaining current value ITHD at time tA2 and the solenoid current value IRL is maintained at the target sustaining current value ITHD at time tA2 and later. That is, the target sustaining current value ITHD continues at time tA2 and later.
As will be apparent from
As set forth above, the current control means 386 sequentially executes the solenoid initial-operation control and the solenoid sustaining current control. Hereunder, detailed description will be provided of how the initial current-supplying time TINT, the target operation initiating current value ITRN and the target sustaining current value ITHD are determined.
On the contrary, the switching electromagnetic solenoid valve 296, shown in
With reference to the relationships shown in
More particularly, the relationship (see
Then, the current control means 386 determines the initial current-supplying time TINT based on the ambient temperature of the switching electromagnetic solenoid valve 104, i.e., the AT oil temperature TEMPOIL by referring to the pre-stored relationship shown in
If the solenoid electric-magnetization determining means 380 determines that the solenoid electrically-magnetizing command is issued, further, the current control means 386 determines the initial current-supplying time TINT and the target operation initiating current value ITRN prior to a step of executing the solenoid initial-operation control. The initial current-supplying time TINT and the target operation initiating current value ITRN may be determined and updated as needed regardless of the determination of the solenoid electric-magnetization determining means 380. Moreover, under a circumstance where the hydraulic control circuit 100, shown in
As shown in
A timing chart for illustrating a variation in the operation initiating current value IRN, when the switching electromagnetic solenoid 102 is current-supplied, i.e., electrically-magnetized in response to the initial current-supplying time TINT, the target operation initiating current value ITRN and the target sustaining current value ITHD determined in such a way mentioned above, is shown in
If the supply pressure PM lies at P1M, the structure “A” has the operation initiating current value IRN lower than that of the structure B as will be understood from
Further, the target sustaining current value ITHD is set to the fixed value regardless of the AT oil temperature TEMPOIL. As will be understood from
First, at step (hereinafter the term “step” will be omitted) 5110 corresponding to the solenoid electric-magnetization determining means 380, a query is made as to whether the solenoid electrically-magnetizing command is made. If the answer to the query at S110 is yes, i.e., when the solenoid electrically-magnetizing command is made, the routine goes to S120. In contrast, if the answer to the query at S110 is no, the routine goes to S160.
At S120 corresponding to the current control means 386, the initial current-supplying time TINT and the target operation initiating current value ITRN are determined based on the AT oil temperature TEMPOIL and the supply pressure PM. More particularly, the target operation initiating current value ITRN is determined based on the supply pressure PM by referring to the relationship (see
At S130 corresponding to the operating-state switching-time determining means 384, a query is made as to whether the initial current-supplying time TINT has elapsed from the solenoid electrically-magnetizing command. That is, a query is made as to whether the initial current-supplying time TINT has elapsed from a time when the answer to S110 is switched from a negative determination to a positive determination. If the answer to S130 is yes, i.e., when the initial current-supplying time TINT has elapsed from the solenoid electrically-magnetizing command, the routine goes to S140. On the contrary, if the answer to S130 is no, the routine goes to S150.
At S140 corresponding to the current control means 386, the solenoid current value IRL is set to the sustaining current value IHD. In this moment, the feedback control is performed to allow the sustaining current value IHD (solenoid current value IRL) to match the target sustaining current value ITHD. In particular, during such a feedback control, a control operation, shown in
At succeeding S220, a control-current correcting amount ΔICON is calculated by referring to the above-mentioned formula (1). At consecutive S230, a product, obtained by adding the control-current correcting amount ΔICON to a control current value I0CON (hereinafter referred to as “preceding control current value I0CON”) at time determined on a preceding state in the flow chart shown in
I
CON
−I0CON+ΔICON (2)
At subsequent S240, the operation is executed to electrically-magnetize the switching electromagnetic solenoid 102 with the control current value ICON updated at S230. That is, the current control element 362 is controlled with the updated control current value ICON, thereby determining the sustaining current value IHD.
At succeeding S250, the control current value ICON updated at S230 is set to be the preceding control current value I0CON as expressed by a formula (3) given below.
I0CON=ICON (3)
Turning back to
At S160 corresponding to the current control means 386, the current control element 362 interrupts the current-supplying of the switching electromagnetic solenoid 102, which is consequently placed in a non-electrically-magnetized state.
The present embodiment has various advantages (A1) to (A11) as listed below.
(A1) With the present embodiment, when the switching electromagnetic solenoid 102 is placed under the electrically-magnetized state, the current control means 386 allows the solenoid current value IRL to be set to the operation initiating current value IRN required for switching the turn-off state to the turn-on during the beginning of the magnetization, whereas after the switching is executed to establish the turn-on, the solenoid current value IRL is set to the sustaining current value IHD lower than the operation initiating current value IRN for sustaining the turn-on. Accordingly, this can reduce the solenoid current value IRL without impairing the operation of the switching electromagnetic solenoid valve 104. As shown in
Further, the minimization of the waste electric current results in the suppression of an increase in temperature of the coil 270 caused by the current-supplying thereof, thereby enabling the suppression of an increase in resistance value of the coil 270 accordingly. Such a reduction in power consumption results in an effective advantage particularly when controllably driving a vehicular power generator (alternator) on a demand to generate electric power, enabling improvement in fuel economy.
(A2) With the present embodiment, further, the reduction in waste electric power as shown in
(A3) With the present embodiment, furthermore, the current control means 386 performs the feedback control such that the sustaining current value IHD approaches the predetermined target sustaining current value ITHD. With the turn-on being sustained, therefore, the sustaining current value IHD is stably converged to the target sustaining current value ITHD, enabling the turn-on to be reliably sustained.
(A4) With the present embodiment, moreover, when the solenoid electrically-magnetizing command is issued, the current control means 386 executes the operation such that the solenoid current value IRL is set to the operation initiating current value IRN until the initial current-supplying time TINT has elapsed from the issuance of the solenoid electrically-magnetizing command while compelling the solenoid current value IRL to be set to the sustaining current value IHD after the elapse of the initial current-supplying time TINT. Accordingly, with the operating-state switching-time determining means 384 making a query as to whether the initial current-supplying time TINT has elapsed, the solenoid current value IRL is lowered in a range from the operation initiating current value IRN to the sustaining current value IHD at appropriate timing, thereby minimizing power consumption of the switching electromagnetic solenoid valve 104.
(A5) The initial current-supplying time TINT is set to an extremely short period of time for the beginning of the magnetization and, hence, mainly lowering the sustaining current value IHD suppresses heat developed in the coil 270 such that the solenoid current value IRL provides almost no adverse affect on heat developed by the coil 270. With the present embodiment, accordingly, mainly lowering the sustaining current value IHD reduces heat developed by the coil 270, and the solenoid current value IRL can be set to the operation initiating current value IRN higher than the sustaining current value IHD during the beginning of the magnetization. This allows the switching electromagnetic solenoid 102 to have an increased electromotive force with almost no increase in a heat value of the coil 270, thereby capable of increasing operating response of the switching electromagnetic solenoid valve 104.
In
(A6) With the present embodiment, besides, the current control means 386 determines the initial current-supplying time TINT based on the AT oil temperature TEMPOIL by referring to the pre-stored relationship shown in
(A7) With the present embodiment, additionally, the current control means 386 determines the initial current-supplying time TINT as shown in
(A8) With the present embodiment, further, the current control means 386 determines the operation initiating current value IRN based on the supply pressure PM by referring to the pre-stored relationship (see
(A9) With the present embodiment, furthermore, the switching electromagnetic solenoid valve 104 takes a structure to allow the spherical valve element 262, actuated by the switching electromagnetic solenoid 102, to communicate the input port 250 and the output port 252 with each other when the switching electromagnetic solenoid 102 is current-supplied. On the contrary, when the switching electromagnetic solenoid 102 is not current-supplied, the spherical valve element 262 closes the input port 250. Therefore, the supply pressure PM, supplied to the input port 250, acts in a direction to facilitate switching the turn-off state to the turn-on.
In this respect, the current control means 386 regulates the operation initiating current value IRN such that the higher the supply pressure PM, the lower will be the operation initiating current value IRN. Therefore, it becomes possible to avoid a pressure (supply pressure) PM of hydraulic oil from adversely affecting mechanical response of the switching electromagnetic solenoid valve 104 in line with the structure of the switching electromagnetic solenoid valve 104. As a result, the switching electromagnetic solenoid valve 104 can ensure stable mechanical response.
(A10) With the present embodiment, moreover, the switching electromagnetic solenoid valve 296 shown in
(A11) With the present embodiment, besides, the initial current-supplying time TINT and the target operation initiating current value ITRN are determined based on the AT oil temperature TEMPOIL and the supply pressure PM in line with the structure of the switching electromagnetic solenoid valve 104. This enables an optimum current control to be performed for an electric current to be controlled with neither excess nor deficiency during the electrically-magnetized state of the switching electromagnetic solenoid 102.
Consecutively, description will be provided of other embodiments according to the present invention. In the following description, like reference characters designate like or corresponding component parts common to those of various embodiments and description of the same is herein omitted.
The first embodiment has been set forth above with reference to a case in which the present invention is applied to the control device of the engine propelled vehicle. On the contrary, the second embodiment will be described below with reference to a case in which the present invention is applied to a control device of a hybrid vehicle. Also, for simplicity of description, description will be provided with a focus on differing points.
Further, the hybrid drive apparatus 510 includes a second motor/generator (hereinafter referred to as “MG2”) as a second drive power source (subsidiary drive power source) capable of selectively executing a power running control to allow drive power to be output for running the vehicle and a regenerative control for recovering energy. The MG2 is connected to the output shaft 514 via an automatic transmission 522. This allows a capacity of torque, transmitted from the MG2 to the output shaft 514, to be incremented or decremented depending on a speed ratio Rs (=rotation speed Nmg2 of MG2/rotation speed Nout of output shaft 514) that is set by the automatic transmission 522.
The automatic transmission 522 is formed in a structure that can establish plural gear positions each having a speed ratios Rs higher than “1”. During a power-running mode in which the MG2 generates torque, the MG2 provides increased torque that can be transferred to the output shaft 514, enabling the MG2 to be structured with a further reduced capacity or in a miniaturized size. With such a structure, if the rotation speed Nout of the output shaft 514 increases with, for instance an increase in vehicle speed, the MG2 is caused to operate at an operating efficiency sustained in a favorable state. To this end, the speed ratio Rs is reduced to cause a drop in the rotation speed Nmg2 of the MG2. In another case where a drop occurs in the rotation sped Nout of the output shaft 514, the speed ratio Rs is caused to increase to increase the rotation speed Nmg2 of the MG2.
During the operation of the automatic transmission 522 under a shifting state, a drop occurs in torque capacity of the automatic transmission 522 or inertia torque occurs due to a fluctuation in rotation speed, resulting in an impact on torque, i.e., output torque of the output shaft 514. Therefore, with the hybrid drive apparatus 510 described above, an operation is executed to control so as to compensate torque of the first drive-force source 512 during the shifting of the automatic transmission 522 for precluding or suppressing a fluctuation in torque of the output shaft 514.
The first drive-force source 512 is structured mainly of an engine 30, a first motor/generator (hereinafter referred to as “MG1”), and a planetary gear unit 526 provided for synthesizing or distributing torque between the engine 30 and the MG1. The engine 30 is a known internal combustion engine, such as a gasoline engine, and a diesel engine, etc., which is structured to have an electronic control device (E-ECU) 528 mainly composed of a microcomputer for performing engine control. The E-ECU 528 is arranged to electrically controlling operating states such as a the throttle opening degree, an air-intake volume, a fuel supply rate and ignition timing, etc. The electronic control device 528 is applied with detection signals from an accelerator depression-stroke sensor 52 operative to detect a depressed stroke of an accelerator pedal 50, and a brake switch 70 to detect the existence or nonexistence of a brake pedal 69 being depressed, etc.
The MG1, composed of, for example, a synchronous electric motor, is structured to selectively perform a function as an electric motor to generate drive torque and another function as an electric power generator. The MG1 is connected to an electricity storage device 532, such as a battery and a capacitor, etc., via an inverter 530. With a motor/generator-controlling electronic control device (MG-ECU) 534 mainly composed of a microcomputer to control the inverter 530, output torque or regenerative torque of the MG1 is adjusted or determined. The electronic control device 534 is supplied with a detection signal from a lever position sensor 74 arranged to detect a shift position of a shift lever 72, and the like.
The planetary gear unit 526 is a single-pinion type planetary gear mechanism operative to perform a known differential action and includes three rotary elements such as a sun gear S0, a ring gear R0 in concentrically meshing engagement with the sun gear S0, and a carrier C0 with which pinions P0 meshing with the sun gear S0 and the ring gear R0 are supported to rotate about their own axes and move around the sun gear S0. The planetary gear unit 526 is disposed to be concentric to the engine 30 and the automatic transmission 522. The planetary gear unit 526 and the automatic transmission 22 have nearly symmetric structures with respect a centerline and, hence, lower half parts thereof are herein omitted from
With the present embodiment, the engine 30 has a crankshaft 536 connected to the carrier C0 of the planetary gear unit 526 via a damper 538. In contrast, the sun gear S0 is connected to the MG1 and the output shaft 14 is connected to the ring gear R0. The carrier C0 functions as an input element; the sun gear S0 functions as a reactive element; and the ring gear R0 functions as an output element.
With the planetary gear unit 526, if reactive torque of the MG1 is input to the sun gear S0 in contrast to output torque of the engine 30 to be input to the carrier C0, the ring gear R0, serving as the output element, bears torque higher than torque input from the engine 30. This causes the MG1 to function as the electric power generator. In addition, with the rotation speed of the ring gear R0, i.e., the rotation speed (output shaft rotation speed) Nout of the output shaft 514 remained constant, causing the rotation speed Nmg1 of the MG1 to fluctuate to be more or lower results in a capability of continuously (infinitely) varying the rotation speed (engine rotation sped) Ne of the engine 30. That is, the operation can be executed to perform a control such that the engine rotation speed Ne is set to, for example, a rotation speed optimum for fuel economy by controlling the MG1. This type of hybrid system is referred to as a mechanical distribution system or a split type.
Turning back to
With the motor/generator-controlling electronic control device (MG-ECU) 534 operating to control the MG2 via the inverter 540, the MG2 is caused to operate as the electric motor or the electric power generator to regulate or determine assist output torque or regenerative torque. The MG2 is connected to the second sun gear S2 and the carrier C1 is connected to the output shaft 514. The first sun gear S1 and the ring gear R1 forms, in combination with the pinions P1 and P2, a mechanism equivalent to a double-pinion type planetary gear unit. Further, the second sun gear S2 and the ring gear R1 forms, in combination with the pinion P2, a mechanism equivalent to a single-pinion type planetary gear unit.
The automatic transmission 522 further includes: a first brake B1 disposed between the first sun gear S1 and a transmission housing 542 for the first sun gear S1 to be selectively fixed; and a second brake B2 disposed between the ring gear R1 and the transmission housing 42 for the ring gear R1 to be selectively fixed. These brakes B1, B2, acting as so-called friction engagement devices operative to generate braking forces due to friction forces, may include multi-plate type engagement devices or band-type engagement devices. Moreover, the brakes B1 and B2 are structured to continuously vary torque capacities depending on engaged pressures resulting from a brake-B1-actuating actuator B1A and a brake-B2-actuating actuator B2A such as hydraulic actuators or the like, respectively.
With the automatic transmission 522 of such a structure as described above, the second sun gear S2 functions as an input element and the carrier C1 functions as an output element. With the first brake B1 caused to engaged, a high-speed gear position H with a speed ratio Rsh higher than “1” is established. With the second brake B2 is caused to engage in place of the first brake B1, a low-speed gear position L with a speed ratio Rsl higher than the speed ratio Rsh of the high-speed gear position H is established. That is, the automatic transmission 522 has a second-stage transmission in which a shifting between the high-speed and low-speed gear positions H and L is executed based on a running condition of the vehicle such as a vehicle speed V and a demanded drive force (or an accelerator's depression-stroke Acc), etc. More particularly, gear position regions are pre-determined as a map (shifting diagram) to allow the automatic transmission 522 to be controlled to set either one of the gear positions depending on detected driving states. An electronic control device (T-ECU) 544 is provided and mainly includes a microcomputer for performing such a control.
The electronic control device 544 is supplied with detection signals from an AT oil temperature sensor 78 for detecting an AT oil temperature TEMPOIL representing a temperature of hydraulic oil, a hydraulic switch SW1 for detecting an engagement hydraulic pressure of the first brake B1, and a hydraulic switch SW2 for detecting an engagement hydraulic pressure of the second brake B2, etc. The electronic control device 544 is further supplied with signals, representing relevant rotation speeds, from a MG2 rotation speed sensor 543 for detecting the rotation speed Nmg2 of the MG2, and an output-shaft rotation speed sensor 545 for detecting the output-shaft rotation speed Nout corresponding to the vehicle speed V. Moreover, the electronic control device 544 corresponds to a control device for a vehicular on/off control valve of the present invention.
With the automatic transmission 522 of such a structure set forth above, if the second brake B2 fixedly secure the ring gear R1, the low-speed gear position L is set and assist torque, output from the MG2, is amplified depending on the speed ratio Rsl with the moment to be additionally applied to the output shaft 514. Causing the first sun gear to be fixedly secured by the first brake B1 in place of the second brake B2 results in the setting of the high-speed gear position H having a speed ratio Rsh lower than the speed ratio Rsl of the low-speed gear position L. Since the speed ratio Rsh of the high-speed gear position H is higher than “1”, assist torque output by the MG2 is amplified in accordance with the speed ratio Rsh to be additionally applied to the output shaft 514.
Under circumstances where the respective gear positions L and H are routinely set, torque additionally applied to the output shaft 514 is equal to torque resulting from increasing output torque of the MG2 depending on the respective speed ratios. Under a shifting transition period of the automatic transmission 522, such torque is reflected on inertia torque occurring due to torque capacities of the brakes B1 and B2 and a fluctuation in rotation speed. In addition, torque additionally applied to the output shaft 514 takes positive torque during a driving state of the MG2 and negative torque during a non-driving state of the same. As used herein, the term “non-driving state of the MG2” refers to a state under which the rotation of the output shaft 514 is transferred through the automatic transmission 522 to the MG2 which in turn is drivably rotated and which does not necessarily involved in a driving or non-driving state of the vehicle 508.
The switching electromagnetic solenoid valve 104 (see
Like the first embodiment, further, even with the hydraulic control circuit 550 of the present embodiment, the switching electromagnetic solenoid valve 296 (see
A line-pressure regulator valve 556, acting as a relief-type pressure regulator valve, includes: a spool valve element 560 that opens and closes between a supply port 556a connected to the line-pressure oil passageway 554; and a discharge port 556b connected to a drain oil passageway 558. Further, the line-pressure regulator valve 556 includes: a control oil chamber 68, accommodating therein a spring 562 for applying a thrust to the spool valve element 560 in a direction to close the same while simultaneously receiving the module pressure PM delivered from a module-pressure oil passageway 566 via the switching electromagnetic solenoid valve 104 when altering a set pressure of the line pressure PL to a higher level; and a feedback oil chamber 570 connected to the line-pressure oil passageway 554 which applies a thrust to the spool valve element 560 in a direction to open the same. Such a structure allows one of a low pressure and a high pressure of two kinds to be output as a constant line pressure PL.
If a demanded output of a driver based on the accelerator's depression-stroke Acc is higher than a predetermined output determining value or if the automatic transmission 522 is placed under the shifting mode, i.e., during a shifting transition mode, then, the switching electromagnetic solenoid valve 104 is switched from a closed state (turn-off state) to an open state (turn-on state). As a result, the modulator pressure PM is supplied to the control oil chamber 568 to increase the thrust force, acting on the spool valve element 560 in the direction to close the same, by a given value such that the line pressure PL is switched from the low pressure state to the high pressure state.
Upon receipt of the line pressure PL as an original pressure, the module-pressure regulator valve 572 outputs a constant module pressure PM, set to be lower than the line pressure PL on a low-pressure side regardless of a fluctuation in the line pressure PL, which is delivered to the module-pressure oil passageway 566. A first linear solenoid valve SL_B1 for controlling the first brake B1 and a second linear solenoid valve SL_B2 for controlling the second brake B2 have valve characteristics of normally closed types (N/C) each of which remains non-current-supplied to place the input port and the output port in a valve-closed state (blocked state). Upon receipt of the module pressure PM as an original pressure, the first and second linear solenoid valve SL_B1 and SL_B2 output control pressures PC1 and PC2 depending on drive currents ISOL1 and ISOL2 representing command values delivered from the electronic control device 544. The resulting control pressures PC1 and PC2 are caused to increase with increases in, for instance, the drive currents ISOL1 and ISOL2.
A B1-control valve 576 includes: a spool valve element 578 for opening or closing a flow path between an input port 576a, connected to the line-pressure oil passageway 554, and an output port 576b that outputs a B1-engagement hydraulic pressure PB1; a control oil chamber 580 receiving a control pressure PC1 from the first linear solenoid valve SL_B1 in order to urge the spool valve element 78 in a opened-valve direction; and a feedback oil chamber 584 accommodating a spring 82 urging the spool valve element 578 in a closed-valve direction while receiving the B1-engagement hydraulic pressure PB1 that is the output pressure. Upon receipt of the line pressure PL as an original pressure, the B1-control valve 576 outputs the B1-engagement hydraulic pressure PB1 at a level depending on the control pressure PC1 delivered from the first linear solenoid valve SL_B1 to be supplied to the first brake B1 via a B1-apply control valve 586 that functions as an interlock valve.
A B2-control valve 590 includes: a spool valve element 592 that opens and closes a flow path between an input port 590a, connected to the line-pressure oil passageway 554, and an output port 590b that outputs a B2-engagement hydraulic pressure PB2; a control oil chamber 594 that receives the control pressure PC2 from the second linear solenoid valve SL_B2 in order to urge the spool valve element 592 in a opened-valve direction; and a feedback oil chamber 598 which accommodates therein a spring 596 that urges the spool valve element 592 in a closed-valve direction while receiving the B2-engagement hydraulic pressure PB2 that is the output pressure. Upon receipt of the line pressure PL in the line-pressure oil passageway 554 as an original pressure, the B2-control valve 590 outputs the B2-engagement hydraulic pressure PB2 at a level, depending on the control pressure PC2 delivered from the second linear solenoid valve SL_B2, which is delivered to the second brake B2 through a B2-apply control valve 600 that functions as an interlock valve.
A B1-apply control valve 586 includes a spool valve element 602 for opening or closing a flow path between an input port 586a, receiving the B1-engagement hydraulic pressure PB1 output from the B1-control valve 576, and an output port 586b connected to the first brake B1. The B1-apply control valve 586 further includes an oil chamber 604, receiving the module pressure PM for urging the spool valve element 602 in the closed-valve direction, and an oil chamber 608 accommodating therein a spring 606 for urging the spool valve element 602 in a closed-valve direction while receiving the B2-engagement hydraulic pressure PB2 output from the B2-control valve 590. The B1-apply control valve 586 is brought into an opened-valve state until the B2-engagement hydraulic pressure PB2 is supplied for engaging the second brake B2. Upon receipt of the B2-engagement hydraulic pressure PB2, the B1-apply control valve 86 is switched to a valve-closed state, thereby preventing the engagement of the first brake B1.
Further, the B1-apply control valve 586 includes a pair of ports 610a and 610b that are closed when the spool valve element 102 is paced in the opened-valve position (at a position on the right side of a centerline shown in
Like the B1-apply control valve 586, the B2-apply control valve 600 also includes a spool valve element 612 that opens and closes a flow path between an input port 600a, receiving the B2-engagement hydraulic pressure PB2 output from the B2-control valve 590, and an output port 600b connected to the second brake B2. The B2-apply control valve 600 further includes an oil chamber 614, applied with the module pressure PM in order to urge the spool valve element 612 in the valve-opened direction, and an oil chamber 618 accommodating therein a spring 616 for urging the spool valve element 612 in the valve-closed direction while applied with the B1-engagement hydraulic pressure PB1 output from the B1-control valve 576. The B2-apply control valve 600 is caused to remain in a valve-opened state until the B2-apply control valve 60 is supplied with the B1-engagement hydraulic pressure PB1 for engaging the first brake B1. Upon receipt of the B1-engagement hydraulic pressure PB1, the B2-apply control valve 600 is switched to the valve-closed state, so that the engagement of the second brake B2 is prevented.
The B2-apply control valve 100 also includes a pair of ports 620a and 620b that are closed when the spool valve element 612 is placed in the valve-opened position (at a position as indicated on the right side of the centerline shown in
The hybrid drive apparatus 510 executes a well-known hybrid running control. That is, after a key is inserted to a key slot, actuating a power switch with a brake pedal depressed in operation results in a startup of the control. Then, a demanded output of a driver is calculated based on the accelerator's depression-stroke Acc to allow the engine 30 and/or the MG2 to generate the demanded output such that the vehicle is driven with a lower amount of exhaust emissions at low fuel consumption. To this end, for instance, a motor running mode achieved mainly by the MG2 acting as the drive force source with the engine 30 rendered inoperative, a charged-power running mode causing the vehicle to run with the MG2 acting as the drive force source while the engine 30 provides a drive power to cause the MG1 to generate electric power, and an engine running mode causing the vehicle to run with the drive power of the engine 30 being mechanically transferred to the drive wheels 40 are switched depending on a running state.
With the engine 30 remained under the driving condition, further, the MG1 controls the engine rotation speed Ne such that the engine 30 operates on an optimum fuel economy curve. Furthermore, when the MG2 is driven to initiate torque assist, the automatic transmission 522 is set to the low-speed gear position L under a condition in which the vehicle speed is low causing increased torque to be applied to the output shaft 14. With an increase in the vehicle speed V, the automatic transmission 522 is set to the high-speed gear position H to relatively lower the rotation speed Nmg2 of the MG2 for achieving a reduction in loss, thereby causing torque assist to be executed with increased efficiency. During the shifting of the automatic transmission 522, for instance, the shifting of the automatic transmission 522 is determined based on the vehicle speed V and the accelerator's depression-stroke Acc or the like by referring to the pre-stored relationship (shifting diagram). Then, the first and second brakes B1 and B2 are controlled so as to switch a gear position determined based on such a determining result. During a coast running, moreover, the MG2 or the MG1 is rotatably driven in response to inertia energy of the vehicle 508 to regenerate electric power, which in turn is stored in the battery 532.
Even with the present embodiment, the control function is applied to the control of the switching electromagnetic solenoid valve 104 or the switching electromagnetic solenoid valve 296 by using the circuit shown in
Especially, during the motor-running mode, almost no probability takes place the electric power to be charged to the battery 532 due the halt of the engine 30. Therefore, executing the solenoid control of the current control means 386 results in a reduction in waste current (see
The first embodiment has been set forth above with reference to a case in which the present invention is applied to the control device with a feedback control which is performed to control the sustaining current value IHD (solenoid current value IRL) so as to coincidence to the predetermined target operation initiating current value ITRN. On the contrary, the third embodiment will be described below with reference to a case in which the present invention is applied to a control device with a feed-forward control which is performed to control the sustaining current value IHD (solenoid current value IRL) to approach the predetermined target operation initiating current value ITRN.
The electromagnetic valve driver circuit 632 of this embodiment corresponds to the electromagnetic valve driver circuit 350 of the first embodiment. The electromagnetic valve driver circuit 632 is constituted similar to the electromagnetic valve driver circuit 350 except that the electromagnetic valve driver circuit 632 has a voltage detector 634 for detecting a output-voltage of the battery 352 instead of the current detector 358. The current control circuit 364 of the electromagnetic valve driver circuit 632 has a switching element for controlling the drive current of the coil 270 by means of controlling a duty of current pulse applied to the coil 270. In this embodiment, the solenoid current IRL, the operation initiating current value IRN, and the sustaining current value IHD are effective values of supplied current to the coil 270 except notice.
The voltage detector 634 detects a output-voltage of the battery 352 which functions as a power source of the electromagnetic solenoid valve 104, and outputs a signal indicating a source voltage VSOL to the coil 270, since the output-voltage of the battery 352 coincides with the source voltage VSOL.
The electronic control device 630 has a current control portion or means 642 instead of the current control means 386, and a map memory means 640.
The map memory portion or means 640 memorizes a current-command map which is pre-set experimentally so as to match the sustaining current value IHD with a predetermined target sustaining current value ITHD. The current-command map indicates a relationship between a duty ratio DTY of the sustaining current value IHD supplying to the solenoid current value IRL, an ambient temperature of the switching electromagnetic solenoid valve 104, and a source voltage VSOL to the coil 270. The duty ratio DTY corresponds to the current-command determined based on the ambient temperature of the switching electromagnetic solenoid valve 104 and the source voltage VSOL in view of the current-command map. The solenoid current IRL of the coil 270 is affected by the ambient temperature of the switching electromagnetic solenoid valve 104 and the source voltage VSOL. The solenoid current IRL increases as the duty ratio DTY is larger. The
As the resistance of the coil 270 increases as the ambient temperature of the switching electromagnetic solenoid valve 104 goes to higher, the solenoid current IRL of the coil 270 decreases with increasing of the ambient temperature as shown in
The current control means 642 is constituted similar to the current control means 386 except that the sustaining current value IHD is controlled by the feed forward control using the current-command map which is pre-set experimentally so as to match the sustaining current value IHD with a predetermined target sustaining current value ITHD.
The feed forward control is as follows. The current control means 642 determine the duty ratio DTY based on the source voltage VSOL detected by the voltage detector 634 and the ambient temperature of the switching electromagnetic solenoid valve 104 by referring to a pre-stored relationship of the current-command map stored in the map memory means 640. For example, the duty ratio DTY36 is determined based on the source voltage V3SOL and the ambient temperature TMP6 in view of the pre-stored relationship of the current-command map shown in
At the step S340 corresponding to the current control means 642, the current to the switching electromagnetic solenoid 102 of the switching electromagnetic solenoid valve 104 is controlled to the sustaining current value IHD in accordance to the duty ratio DTY determined by the feed forward control utilized the current-command map stored in the in the map memory means 640. The feed forward control shown in the step S340 is executed repeatedly.
At the step S410 of
At the step S430 of
At the step S440 of
The present embodiment has various advantages as same as the advantages (A1) to (A2) and (A4) to (A11) of the first embodiment. The current control means 642 determines the duty ratio DTY based on the source voltage VSOL and the ambient temperature of the switching electromagnetic solenoid valve 104 referring to a pre-stored relationship of the current-command map stored in the map memory means 640, which is pre-set experimentally so as to allow the sustaining current value IHD to match the target sustaining current value ITHD. As the current control means 642 controls the sustaining current value IHD to match the target sustaining current value ITHD by means of the above feed forward control, the waste electric current is minimized to be lower than that achieved with the related art on/off control, minimizing power consumption of the switching electromagnetic solenoid valve 104, with a simple current control means compared to the first embodiment.
In the foregoing, although the present invention has been described above with reference the embodiments shown in the accompanying drawings, it is intended that the embodiments described be considered only as illustrative of the present invention and that those skilled in the art can implement the present invention in modes with various modifications and improvements.
For instance, while with the first and second embodiment described above, the current control element 362 shown in
With the first to third embodiments discussed above, further, while the electromagnetic valve driver circuit 350, 632 is provided independently of the switching electromagnetic solenoid valve 104 in
With the first and second embodiments discussed above, furthermore, the electric-magnetization states of the switching electromagnetic solenoid valves 104 and 296 may be controlled on direct currents or may be subjected to duty controls. For instance, when performing the duty controls of the switching electromagnetic solenoid valves 104 and 296, the timing chart indicated by the broken line L01 in
With the first to third embodiments discussed above, moreover, the switching electromagnetic solenoid valve 104 takes a structure in which with the input port 250 remained in the closed state, the urging force is applied to the spherical valve element 262 in opposition to the supply pressure PM applied to the input port 250 to sustain such a closed state. However, the present invention is not limited to such a structure provided that the electromagnetic valve controlled with the control device of the present invention, is an on/off valve of the type that is placed in an operating state switched between a turn-on state and a turn-off state depending on the electrically-magnetization or non-electrically-magnetizing of the solenoid. The switching electromagnetic solenoid valve 104 may include, for instance, an electromagnetic type directional control valve having a spool valve element formed with a communication recess for establishing a communicating state or a non-communicating state between respective ports or a two-way valve.
While with the first and second embodiment shown in
While with the first and second embodiment shown in
While with the flow chart for the first and second embodiment shown in
While at S150 of the first and second embodiment shown in
With the first and second embodiments described above, if the control current value ICON is set to allow the maximum current to supply through the current control element 362 until the initial current-supplying time TINT elapses from the solenoid electrically-magnetizing command such that the operation initiating current value IRN is uniquely determined based on resistance values of the coils 270 and 322 and a predetermined coil applied voltage applied to the coils 270 and 322. In such a case, the coil applied voltage is determined on experimental tests so as to obtain the operation initiating current value IRN to enable the turn-off state to be switched to the turn-on state even under a circumstance where the resistance values of the coils 270 and 322 are maximized depending on usage states.
Further, while the first embodiment has been described above with reference to a case where the present invention is applied to the normal engine-propelled vehicle and the second embodiment has been described above with reference to a case in which the present invention is applied to the hybrid vehicle, the structure of the vehicle is not particularly limited and the present invention may be applicable to, for instance, an electric vehicle.
Furthermore, it can be also conceived that the present invention is applicable to control the on/off control valve incorporated in the hydraulic pressure control circuit for performing a shifting control of a CVT.
With the first to third embodiments mentioned above, moreover, the switching electromagnetic solenoid valves 104 and 296 are employed in the hydraulic control circuits 100 and 550 of the automatic transmissions 10 and 522, respectively, usages of those valves are not limited to those for hydraulic pressure controls of the automatic transmissions 10 and 522.
With the first and second embodiments mentioned above, besides, the current control means 386 determines the initial current-supplying time TINT based on the AT oil temperature TEMPOIL and determines the operation initiating current value IRN (the target operation initiating current value ITRN) based on the supply pressure PM applied to the switching electromagnetic solenoid valve 104. However, the operation initiating current value IRN (the target operation initiating current value ITRN) may be determined based on the AT oil temperature TEMPOIL and the initial current-supplying time TINT may be determined based on the supply pressure PM. In such a case, the current control means 386 executes a control such that the lower the AT oil temperature TEMPOIL, the higher will be the operation initiating current value IRN (the target operation initiating current value ITRN). In addition, the control is executed such that the higher the supply pressure PM, the longer will be the initial current-supplying time TINT.
With the first and second embodiments mentioned above, the current control means 386 may be arranged to determine the initial current-supplying time TINT and the operation initiating current value IRN (the target operation initiating current value ITRN) based on both of the AT oil temperature TEMPOIL and on the supply pressure PM applied to the switching electromagnetic solenoid valve 104. In an alternative, the initial current-supplying time TINT and the operation initiating current value IRN (the target operation initiating current value ITRN) may be determined based on either one of the AT oil temperature TEMPOIL and the supply pressure PM applied to the switching electromagnetic solenoid valve 104. In addition, the relationship between the AT oil temperature TEMPOIL, the initial current-supplying time TINT and the operation initiating current value IRN (the target operation initiating current value ITRN) has no need to be continuous and such a relationship may vary in a stepwise relationship in the order of, for instance, about a two-stage or a three-stage.
With the first to third embodiments mentioned above, additionally, although the initial current-supplying time TINT and the operation initiating current value IRN (the target operation initiating current value ITRN) are determined based on both of the AT oil temperature TEMPOIL and the supply pressure PM, it doesn't matter if the initial current-supplying time TINT and the operation initiating current value IRN (the target operation initiating current value ITRN) are pre-determined to lie at, for instance, a fixed value with no regard to the AT oil temperature TEMPOIL or the supply pressure PM.
While
Moreover, during the solenoid control of the first to third embodiment set forth above, the solenoid current value IRL drops from the operation initiating current value IRN to the sustaining current value IHD due to the elapse of the initial current-supplying time TINT. The elapse of such a time is not essential to be a criteria for the drop in the solenoid current value IRL. For instance, positions of the plungers 264 and 314 may be detected to provide plunger positions, based on which the operation may be executed to lower the solenoid current value IRL from the operation initiating current value IRN to the sustaining current value IHD.
With the third embodiments mentioned above, the duty ratio DTY of the sustaining current value IHD (solenoid current value IRL) is used as the current-command of the sustaining current of the switching electromagnetic solenoid valve 104, however, it doesn't matter if other parameter is used as the current-command of the sustaining current of the switching electromagnetic solenoid valve 104.
With the first to third embodiments mentioned above, at least two of the three embodiments may be combined each other.
Besides, although no individual illustrations are made, the present invention may be implemented in various modifications without departing from the scope of the present invention.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2009-004128 | Jan 2009 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2010/050190 | 1/5/2010 | WO | 00 | 6/22/2011 |
