Automatic start controlling apparatus of internal combustion engine and detector for detecting engagement of clutch

The present invention relates to an automatic start controlling apparatus and a detector for detecting engagement of a clutch of an internal combustion engine. Particularly, the present invention pertains to an automatic start controlling apparatus and a clutch engagement detector of an internal combustion engine having a transmission that includes a clutch actuated by a drive source other than the engine when the engine is not running.

Japanese Unexamined Patent Publication No. 9-71138 discloses an economy running system. The system automatically stops the engine when the vehicle stops, for example, at an intersection, and automatically starts the engine by actuating a starter when the vehicle is started. The system includes an automatic transmission that has a clutch.

To quickly start the vehicle after the engine is automatically stopped by the system, the automatic transmission is preferably engaged when the engine is not running. That is, the automatic transmission preferably receives hydraulic pressure regardless of whether the engine is running. The system disclosed in Japanese Unexamined Patent Publication No. 11-147424 has a battery powered electric oil pump, which generates hydraulic pressure and applies the pressure to an automatic transmission. The system disclosed in Japanese Unexamined Patent Publication No. 8-14076 includes an accumulator, which stores hydraulic pressure to maintain a clutch engaged so that the vehicle can be quickly started after an automatic stop procedure.

Even if an economy running system has an electric oil pump or an accumulator, the clutch engagement may be inadequate after the engine is automatically stopped. For example, if air is caught in the oil, if the oil pump is frozen or if a conducting wire is broken, a sufficient hydraulic pressure cannot be generated and sufficient engagement of the clutch cannot be maintained.

If the engagement of the clutch is insufficient after the engine is automatically stopped, the pump of the automatic transmission starts applying sufficient hydraulic pressure to the clutch when the engine is started, which suddenly engages the clutch. The sudden engagement of the clutch creates shock and thus disturbs the driver. Particularly, if the clutch is suddenly engaged after the driver steps on the acceleration pedal, a relatively great shock is created.

Accordingly, it is an objective of the present invention to provide an automatic start controlling apparatus for an internal combustion engine having an automatic transmission that reduces shock when the clutch is engaged. Another objective is to provide a detector that detects the engagement of the clutch without any additional sensor.

To achieve the above objective, the present invention provides an automatic start controlling apparatus for automatically starting an internal combustion engine coupled to a transmission. The transmission has an input shaft connected to the engine, an output shaft, and a clutch located between the input and output shafts. The clutch is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The clutch is actuated by a drive source other than the engine when the engine stops. The automatic start controlling apparatus has a controller. When the engine is automatically started, the controller detects whether the clutch is completely engaged. When the controller judges that the clutch is partially engaged, the controller reduces the output torque of the engine or limits an increase of the output torque.

The present invention also provides an automatic start controlling apparatus for automatically starting an internal combustion engine coupled to a transmission. The transmission has an input shaft connected to the engine, an output shaft, and a clutch located between the input and output shafts. The clutch is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The clutch is actuated by a drive source other than the engine when the engine stops. The automatic start controlling apparatus has a controller. When the engine is automatically started, the controller detects whether the clutch is completely engaged. When the controller detects that the clutch is partially engaged, the controller controls the clutch to gradually and completely engage.

The present invention also provides a detecting apparatus for detecting an engagement state of a clutch. The clutch is included in a transmission coupled to an internal combustion engine. The transmission has an input shaft, which is connected to the engine, and an output shaft. The clutch is located between the input shaft and the output shaft and is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The clutch is actuated by a drive source other than the engine when the engine stops. The detecting apparatus comprises means for determining whether the running state of the engine satisfies a predetermined automatic start condition while the drive source actuates the clutch to engage the clutch, and means for detecting whether the clutch is completely engaged based on the rotation of the input shaft of the transmission when the determining means determines that the condition is satisfied.

The present invention also provides a detecting apparatus for detecting an engagement state of a clutch. The clutch is included in a transmission coupled to an internal combustion engine. The transmission has an input shaft, which is connected to the engine, and an output shaft. The clutch is located between the input shaft and the output shaft and is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The clutch is actuated by a drive source other than the engine when the engine stops. The detecting apparatus comprises means for determining whether the running state of the engine satisfies a predetermined automatic start condition while the drive source actuates the clutch to engage the clutch, and means for detecting whether the clutch is completely engaged based on the rotation speed of the input shaft, the rotation speed of the output shaft and a gear ratio of the transmission when the determining means determines that the condition is satisfied.

The present invention also provides a method for automatically starting an internal combustion engine coupled to a transmission. The transmission has an input shaft connected to the engine, an output shaft, and a clutch located between the input and output shafts. The clutch is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The method comprises actuating the clutch by a drive source other than the engine when the engine stops, detecting whether the clutch is completely engaged when the engine is automatically started, and reducing the output torque of the engine or limiting an increase of the output torque when detecting detects that the clutch is partially engaged.

The present invention also provides a method for automatically starting an internal combustion engine coupled to a transmission. The transmission has an input shaft connected to the engine, an output shaft, and a clutch located between the input and output shafts. The clutch is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The method comprises actuating the clutch by a drive source other than the engine when the engine stops, detecting whether the clutch is completely engaged when the engine is automatically started, and controlling the clutch to gradually and completely engage when the detecting detects that the clutch is partially engaged.

The present invention also provides a detecting method for detecting an engagement state of a clutch, wherein the clutch is included in a transmission coupled to an internal combustion engine. The transmission has an input shaft, which is connected to the engine, and an output shaft. The clutch is located between the input shaft and the output shaft and is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The method comprises actuating the clutch by a drive source that differs from the engine when the engine stops, determining whether the running state of the engine satisfies a predetermined automatic start condition while the drive source actuates the clutch to engage the clutch, and detecting whether the clutch is completely engaged based on the rotation of the input shaft of the transmission when determining that the condition is satisfied.

The present invention also provides a detecting method for detecting an engagement state of a clutch. The clutch is included in a transmission coupled to an internal combustion engine. The transmission has an input shaft, which is connected to the engine, and an output shaft. The clutch is located between the input shaft and the output shaft and is engaged to transmit the output torque of the engine from the input shaft to the output shaft. The method comprises actuating the clutch by a drive source that differs from the engine when the engine stops, determining whether the running state of the engine satisfies a predetermined automatic start condition while the drive source actuates the clutch to engage the clutch, and detecting whether the clutch is completely engaged based on the rotation speed of the input shaft, the rotation speed of the output shaft and a gear ratio of the transmission when determining that the condition is satisfied.

Other aspects and advantages of the invention will become apparent from the following description, taken in conjunction with the accompanying drawings, illustrating by way of example the principles of the invention.

The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:

FIG. 1 is a schematic diagram illustrating an engine and a controller according to a first embodiment of the present invention;

FIG. 2 is a schematic diagram illustrating the structure of the automatic transmission shown in FIG. 1;

FIG. 3 is a chart showing the operation of the automatic transmission shown in FIG. 1;

FIG. 4 is a flowchart showing an automatic stop procedure executed by the ECU shown in FIG. 1;

FIG. 5 is a flowchart showing an automatic start procedure executed by the ECU shown in FIG. 1;

FIG. 6 is a flowchart showing a procedure for reducing shock caused by engagement of a clutch in the procedure of FIG. 5;

FIG. 7 is a flowchart showing a procedure for changing the throttle opening degree TA;

FIG. 8 is a timing chart showing an operation when the electric oil pump of FIG. 1 is generating sufficient hydraulic pressure;

FIG. 9 is a timing chart showing an operation when the electric oil pump of FIG. 1 is generating insufficient hydraulic pressure;

FIG. 10 is a timing chart like FIG. 9;

FIG. 11 is a schematic diagram illustrating a controller according to a second embodiment;

FIG. 12 is a flowchart showing a procedure executed by an ECU for determining the power transmitting state of the clutch according to a third embodiment;

FIG. 13 is a flowchart showing a procedure executed by an ECU for determining the power transmitting state of the clutch according to a fourth embodiment; and

FIG. 14 is a flowchart showing a procedure executed by an ECU for determining that the transmitting state is abnormal.

FIG. 15 is a flowchart showing a procedure like FIG. 6, according to a fifth embodiment; and

FIG. 16 is a flowchart showing a procedure like FIG. 6, according to a sixth embodiment.

An internal combustion gasoline engine 2 and a controller according to a first embodiment of the present invention will now be described with reference to FIGS. 1 to 10 . The engine 2 is used for driving a vehicle.

Power of the engine 2 is transmitted to an output shaft 6 b through a crankshaft 2 a of the engine, a torque converter 4 and an automatic transmission 6 . Power is then transmitted to vehicle wheels (not shown). Power of the engine 2 is also transmitted to a belt 14 through an electromagnetic clutch 10 , which is coupled to the crankshaft 2 a , and a main pulley 12 . Power that is transmitted to the belt 14 rotates first, second and third pulleys 16 , 18 , 20 . The electromagnetic clutch 10 selectively transmits power from the crankshaft 2 a to the main pulley 12 .

A power steering pump 22 is driven by power that is transmitted through the first pulley 16 . A compressor 24 in an air conditioner is drive by power that is transmitted through the second pulley 18 . A motor-generator 26 is driven by power that is transmitted through the third pulley 20 . The motor-generator 26 is electrically connected to an inverter 28 . The inverter 28 is switched to selectively charge a battery 30 . When the engine 2 is not running and the motor-generator 26 functions as a motor, the inverter 28 adjusts electric energy supplied from the battery 30 to the motor-generator 26 to control the speed of the motor-generator 26 .

The automatic transmission 6 includes an oil pump, which is actuated by the engine 2 . The oil pump supplies oil to a hydraulic pressure controller 6 a . Supplied oil is sent to clutches C 0 , C 1 , C 2 and brakes B 0 , B 1 , B 2 , B 3 , B 4 , which are located in the automatic transmission 6 as shown in FIG. 2, through a control valve in the controller 6 a . Accordingly, the operation of the clutches C 0 to C 2 , the brakes B 0 to B 4 and one-way clutches F 0 , F 1 , F 2 is controlled. The speed NAO of the output shaft 6 b of the automatic transmission 6 is detected by a first speed sensor 32 . The turbine speed NCO, or the speed of an input shaft 6 c , of the automatic transmission 6 is detected by a second speed sensor 34 through a front sun gear.

An electric oil pump 36 also supplies oil to the hydraulic pressure controller 6 a of the automatic transmission 6 . Therefore, when the engine 2 is not running, the oil pump 36 actuates the clutches C 0 to C 2 , the brakes B 0 to B 4 and the one-way clutches F 0 to F 2 . In this embodiment, the automatic transmission 6 , the hydraulic controller 6 a , and the oil pump 36 form a power transmission mechanism.

An electronic control unit (ECU) 38 is connected to the first and second speed sensors 32 , 34 . The ECU 38 is also connected to an idle switch 50 , an acceleration pedal depression degree sensor 52 , a throttle opening degree sensor 54 , a shift lever position sensor 56 , an engine speed sensor 58 , a system switch 60 , an air conditioner switch 62 , a brake switch 64 and a coolant temperature sensor 66 .

When an acceleration pedal is depressed, the idle switch 50 is turned off. When the acceleration pedal is not depressed, the idle switch 50 is turned on. A signal indicating the on-off state of the idle switch 50 is sent to the ECU 38 . The acceleration pedal depression degree sensor 52 detects the acceleration pedal depression degree ACCP. The detected signal is sent to the ECU 38 .

The throttle sensor 54 detects the opening degree of a throttle valve 2 c . The detected signal is sent to the ECU 38 . The throttle valve 2 c is located in an intake passage 2 b of the engine 2 to adjust the flow rate of air that is drawn into the engine 2 . The shift position sensor 56 detects the shift position SHFT of the automatic transmission 6 . The detected signal is sent to the ECU 38 . The engine speed sensor 58 detects the speed NE of the engine 2 . The detected signal is sent to the ECU 38 .

As a driver turns the system switch 60 on and off, the economy running system is started and stopped. On-off signals of the system switch 60 are sent to the ECU 38 . As the driver turns the air conditioner switch 62 on and off, the air conditioner is started and stopped. On-off signals of the air conditioner switch 62 are sent to the ECU 38 . When the brake pedal is depressed, the brake switch 64 is turned on. When the brake pedal is not depressed, the brake switch 64 is turned off. On-off signals of the brake switch 64 are sent to the ECU 38 . The coolant temperature sensor 66 detects the coolant temperature THW of the engine 2 . The detected signal is sent to the ECU 38 .

The main part of the ECU 38 includes a microcomputer. The microcomputer includes a read only memory (ROM) and a random access memory (RAM). The ECU 38 executes various computations in accordance with the programs stored in the ROM. Based on the results of the computation, the ECU 38 actuates a throttle valve motor 2 d , the hydraulic controller 6 a , the electromagnetic clutch 10 , the inverter 28 , the electric oil pump 36 , the starter 40 , a fuel injector 42 and an igniter (not shown). Accordingly, the engine 2 and the automatic transmission 6 are controlled. The throttle valve motor 2 d adjusts the opening degree TA of the throttle valve 2 c . The fuel injector 42 injects fuel into the intake port (not shown) of the engine 2 . Alternatively, the engine 2 may have multiple fuel injectors 42 , each of which inject fuel into the associated combustion chamber (not shown).

An automatic stop procedure, automatic start procedure, shock reduction procedure and throttle opening degree changing procedure, which are executed by the ECU 38 , will now be described. The automatic stop procedure and the automatic start procedure are executed when the system switch 60 is turned on by the driver.

FIG. 4 shows a flowchart of the automatic stop procedure. This procedure is executed at predetermined intervals. In step S 110 , running state of the engine 2 is detected. For example, the coolant temperature THW, which is detected by the coolant temperature sensor 66 , the depression state of the acceleration pedal, which is detected by the idle switch 50 , the voltage of the battery 30 , the depression state of the brake pedal, which is detected by the brake switch 64 and the vehicle speed SPD, which is computed based on the detection value of the first speed sensor 32 , are stored in the RAM of the ECU 38 .

In step S 120 , the ECU 38 judges whether the following conditions (1) to (5) are satisfied. Condition (1) refers to a state of the engine 2 in which the engine 2 is warm and is not overheated (the coolant temperature THW is lower than an upper limit value THWmax and higher than a lower limit value THWmin). Condition (2) refers to a state in which the acceleration pedal is not depressed (the idle switch 50 is on). Condition (3) refers to a state in which the charge level of the battery 30 is equal to or greater than a predetermined level (the voltage of the battery 30 is equal to or greater than a referential level). Condition (4) refers to a state in which the brake pedal is depressed (the brake switch 64 is on). The condition (5) refers to a state in which the vehicle is not moving (the vehicle speed SPD is 0 km/h). When conditions (1) to (5) are satisfied, the ECU 38 judges that the automatic stop condition is satisfied.

If the outcome of step S 120 is negative, or when one or more of the conditions (1) to (5) are not satisfied, the ECU 38 judges that the automatic stop condition is not satisfied and terminates the procedure.

When the conditions (1) to (5) are satisfied, the outcome of step S 120 is positive and the ECU 38 proceeds to step S 130 . In step S 130 , the ECU 38 stops the engine 2 . For example, fuel injection from the fuel injector 42 and the ignition of air-fuel mixture in the combustion chamber by the ignition plug are stopped, which immediately stops the engine 2 . The ECU 38 then terminates the procedure. In step S 130 , the electric oil pump 36 is started.

FIG. 5 shows a flowchart of the automatic start procedure. This procedure is executed at predetermined intervals. In step S 210 , the running state of the engine 2 is detected for determining whether the procedure needs to be started. The data is stored in the RAM of the ECU 38 .

In this embodiment, for example, the data that is stored in the RAM in step S 110 of FIG. 4, or the coolant temperature THW, the acceleration pedal depression degree ACCP, the voltage of the battery 30 , the on-off state of the brake witch 64 and the vehicle speed SPD, are stored in the RAM.

If at least one of the conditions (1) to (5) is not satisfied in step S 220 , the ECU 38 judges that the automatic start condition is satisfied.

In addition to the conditions (1) to (5), other conditions may be considered. Alternatively, one or more conditions may be deleted from the conditions (1) to (5).

If the outcome of step S 220 is negative, that is, if the engine 2 was not stopped by the automatic stop procedure, the automatic start condition is not satisfied and the ECU 38 terminates the procedure. Also, if all the conditions (1) to (5) are satisfied, the automatic start condition is not satisfied and the ECU 38 terminates the procedure.

If one or more of the conditions (1) to (5) are not satisfied after the engine 2 is stopped by the automatic stop procedure, that is, when the outcome of step S 220 is positive, the ECU 38 proceeds to step S 230 . In step S 230 , the ECU 38 starts the automatic start procedure and, thereafter, temporarily suspends the procedure.

In step S 230 , the starter 40 is actuated to rotate the crankshaft of the engine 2 . Further, a fuel injection procedure for starting the engine 2 and an ignition timing control procedure for starting the engine 2 are performed so that the engine 2 is automatically started. When the engine 2 is started, a normal fuel injection control procedure and a normal ignition timing control procedure and other procedures for running the engine 2 are started. When the hydraulic pressure generated by the oil pump in the automatic transmission 6 increases to a sufficient level by the operation of the engine 2 , the electric oil pump 36 is stopped.

When the engine 2 is automatically started in step S 230 , the shock of engagement of the clutch C 1 is reduced by a procedure shown in FIG. 6 . The procedure of FIG. 6 is performed at predetermined short intervals. In step S 310 , the speed NAO of the output shaft 6 b of the automatic transmission 6 , the turbine speed NCO, the shift position SHFT of the automatic transmission 6 , the on-off state of the idle switch, the throttle opening degree TA, the acceleration pedal depression degree ACCP, the engine speed NE and the vehicle speed SPD are stored in the working area of the RAM in the ECU 38 .

In step S 320 , the ECU 38 judges whether the engine 2 is being started according to step S 230 . If the engine 2 is not being started by the automatic start procedure, or if the outcome of step S 320 is negative, the ECU 38 proceeds to step S 330 . In step S 330 , the ECU 38 sets an output limiting flag FS to OFF and temporarily suspends the current routine. If the engine 2 is being started by the automatic start procedure, or if the outcome of step S 320 is positive, the ECU 38 proceeds to step S 340 . In step S 340 , the ECU 38 judges whether the shift position SHFT is D, which is shown in FIG. 3 . If the shift position SHFT is not D, or if the outcome of step S 340 is negative, the ECU 38 proceeds to step S 330 . In step S 330 , the ECU 38 sets the output restriction flag FS to OFF and temporarily suspends the current routine.

If the current shift position SHFT is D, the outcome of step S 340 is positive. That is, the ECU 38 judges that engine 2 was automatically started while power of the engine 2 was transmitted from the input shaft 6 c to the output shaft 6 b of the automatic transmission 6 . Thereafter, the ECU 38 proceeds to step S 350 . In step S 350 , the ECU 38 judges whether the clutch C 1 of the automatic transmission 6 is slipping based on the turbine speed NCO, which is detected by the second speed sensor 34 , the output shaft speed NAO, which is detected by the first speed sensor 32 , and a gear ratio Gr, which corresponds to the shift position of the automatic transmission 6 . If the clutch C 1 is not slipping, the following equation (1) is satisfied.

NCO=NAO×Gr   (1)

If the clutch C 1 is slipping, the equation (2) is satisfied.

NCO>NAO×Gr   (2)

Immediately after the automatic start procedure is initiated, the crankshaft of the engine is about to be rotated by the starter 40 . At this time, the turbine speed NCO, the output shaft speed NAO are both 0 rpm regardless of the engage state of the clutch C 1 . In this state, the equation (1) is satisfied. Accordingly, the outcome of step S 350 is negative, and the ECU 38 proceeds to step S 360 . In step S 360 , the ECU 38 judges whether the output limiting flag FS is ON. Since the ECU 38 set the flag FS to OFF in step S 330 , the outcome of step S 360 is negative. Then, the ECU 38 proceeds to step S 370 . In step S 370 , the ECU 38 starts controlling the hydraulic pressure in the automatic transmission 6 in a manner for economy running. Thereafter, the ECU 38 temporarily terminates the procedure.

During the automatic start procedure, the hydraulic pressure controller 6 a maximizes the hydraulic pressure applied to the clutch C 1 when the clutch C 1 engages to quickly increase the torque capacity of the clutch C 1 . Therefore, if the electric oil pump 36 applies sufficient hydraulic pressure to the clutch C 1 during the automatic stop procedure, the engagement of the clutch C 1 is maintained continuously after the procedure.

If the engine 2 is started while the electric pump 36 is applying sufficient hydraulic pressure to the automatic transmission 6 and the clutch C 1 is not slipping in the automatic start procedure, that is, if the outcome of step S 320 is negative, the ECU 38 sets the output limiting flag FS to OFF in step S 330 . Then, the ECU 38 temporarily suspends the current routine. After the engine 2 is started, the hydraulic pressure in the automatic transmission 6 is controlled by the oil pump in the automatic transmission 6 . Therefore, the ECU 38 stops the electric oil pump 36 when the hydraulic pressure of the oil pump in the automatic transmission 6 is sufficient.

If the clutch C 1 slips during the automatic start procedure due to insufficient hydraulic pressure applied to the automatic transmission 6 by the electric oil pump 36 , that is, if the outcome of step S 350 is positive, the ECU 38 proceeds to step S 380 . In step S 380 , the hydraulic pressure in the automatic transmission 6 is controlled in the same manner as when the shift position SHFT is changed from the N to the D in a normal driving mode. In step S 380 , the clutch C 1 is gradually engaged to reduce the shock of engagement. Therefore, after the hydraulic pressure to the clutch C 1 is maximized in step S 370 , the ECU 38 duty controls the electromagnetic valve in the hydraulic controller 6 a to temporarily lower the hydraulic pressure and then gradually increases the hydraulic pressure applied to the clutch C 1 . Thus, when the hydraulic pressure generated by the oil pump of the automatic transmission 6 is increased, the clutch C 1 is not abruptly engaged. Accordingly, the shock caused by engagement of the clutch C 1 is reduced.

Once executed, step S 380 is not repeated in the same cycle. That is, step S 380 is performed only when steps S 320 , S 340 , S 350 are satisfied after the automatic start control is started each time. Step S 380 will be performed when steps S 320 , S 340 , S 350 are satisfied in the subsequent automatic start control.

In step S 390 , the ECU 38 judges whether the idle switch 50 is off. If the idle switch 50 is on, the outcome of step S 390 is negative and the ECU 38 proceeds to step S 330 . In step S 330 , the ECU 38 sets the output limiting flag FS to OFF and temporarily suspends the current routine. Thereafter, if the idle switch 50 remains on, the hydraulic pressure applied to the clutch C 1 by the automatic transmission 6 is sufficient, and the clutch C 1 does not slip, the outcome of step S 350 will be negative. In this case, the ECU 38 proceeds to step S 360 . In step S 360 , since the flag FS is set at OFF, the outcome is negative and the ECU 38 proceeds to step S 370 . In step S 370 , the ECU 38 controls the hydraulic pressure supplied to the automatic transmission 6 and temporarily suspends the current routine.

If the driver steps on the acceleration pedal while the clutch C 1 is slipping, the idle switch 50 is turned off. In this case, the outcome of step S 390 is positive. Also, if the idle switch 50 is off when the automatic start control is started, the outcome of the ECU 38 is positive. In these cases, the ECU 38 proceeds to step S 400 . In step S 400 , the ECU 38 starts limiting the throttle opening degree TA. That is, the ECU 38 starts a procedure for delaying the increase of the throttle opening degree TA.

The throttle opening TA is limited based on a target value TAt of the throttle opening degree TA, which is computed in the flowchart of FIGS. 6 and 7.

In step S 400 , the ECU 38 starts controlling the throttle opening degree TA. Then, the ECU 38 proceeds to step S 410 . In step S 410 , the target value TAt of the throttle opening degree TA, which is used for controlling the opening degree of the throttle valve 2 c , is set to an idle throttle opening degree TAecoidl. In this embodiment, the idle throttle opening degree TAecoidl is zero percent (TAecoidl=0%). As long as the engagement shock of the clutch C 1 is reduced when the hydraulic pressure from the oil pump in the automatic transmission 6 is increased to completely engage the clutch C 1 , the idle throttle opening degree TAecoidl may be greater than zero percent.

In step S 420 , the ECU 38 sets the output limiting flag FS to ON and temporarily suspends the current routine.

In step S 410 , the ECU 38 maintains the throttle opening degree TA at zero percent until the clutch C 1 does not slip even if the driver steps on the acceleration pedal. Thereafter, when the hydraulic pressure of the oil pump in the automatic transmission 6 is sufficient and therefore the clutch C 1 does not slip, the outcome of step S 350 is negative. In this case, the ECU 38 proceeds to step S 360 . Since the flag FS is ON, the outcome of step S 360 is positive. In step S 430 , the ECU 38 sets a flag FA to ON, which starts changing the throttle opening degree TA. Then, the ECU 38 temporarily suspends the current routine.

A control procedure for changing the throttle opening degree TA will now be described with reference to FIG. 7 . The routine of FIG. 7 is executed every predetermined intervals. In step S 510 , the ECU 38 judges whether the flag FA is ON. If step S 430 of FIG. 6 has not been executed and the flag FA is OFF, the outcome of step S 510 is negative. In this case, the ECU 38 temporarily suspends the current routine.

If the flag FA is set to ON in step S 430 , the outcome is positive and the ECU 38 proceeds to step S 520 . In step S 520 , a target value TAt of the throttle opening degree TA is computed by referring to the following equation (3).

TAt=TAt+TARECO   (3)

The ECU 38 adds the value TARECO to the current target throttle opening degree TAt to obtain a new target degree TAt. The value TARECO represents an amount of opening degree that is required in each routine for changing the target throttle opening degree TAt to a value that corresponds to a normal running state of the engine 2 .

In step S 530 , a throttle opening TAtorg, which is used in a normal control procedure, is obtained from a map that is computed based on the acceleration pedal depression degree ACCP. In addition to the acceleration pedal depression degree, the map may have other parameters that represent the running state of the engine 2 .

In step S 540 , the ECU 38 judges whether the target value TAt of the throttle pedal opening degree TA is equal to greater than the throttle opening degree TAtorg. If the throttle opening degree TAt is less than the throttle opening TAtorg (TAt<TAtorg), the outcome of step S 540 is negative. In this case, the ECU 38 temporarily suspends the current routine.

If the throttle opening TAt is equal to or greater than the throttle opening TAtorg (TAt≧TAtorg), the outcome of step S 540 is positive, and the ECU 38 proceeds to step S 550 . In step S 550 , the ECU 38 stops the procedure for limiting the throttle opening degree TA. That is, the ECU 38 starts controlling the opening degree of the throttle valve 2 c referring to the map, which is based on the acceleration pedal depression degree ACCP.

In step S 560 , the ECU 38 sets the flag FA to OFF and terminates the routine.

One example of the above described procedure will now be described with reference to timing charts of FIGS. 8 to 10 . FIG. 8 shows a case when the hydraulic pressure generated by the electric pump 36 is normal during the automatic stop procedure of the engine 2 . The brake switch is turned off at time t 1 . At this time, the turbine speed NCO and the output shaft speed NAO are 0 rpm. In this case, the ECU 38 judges that the clutch C 1 is not slipping. That is, the outcome of step S 350 is negative. Therefore, the throttle opening TA and the duty ratio for the electromagnetic valve are controlled according to the normal economy running control of step S 370 .

FIG. 9 shows a case where the hydraulic pressure generated by the electric oil pump 36 is insufficient during the automatic stop procedure of the engine 2 . During the period from time t 13 to t 14 , the turbine speed NCO changes despite that the output shaft speed NAO is 0 rpm. Thus, the ECU 38 judges that the clutch C 1 is slipping. In this case, in step S 380 of FIG. 6, the ECU 38 changes the hydraulic pressure applied to the automatic transmission 6 in the same manner as when the shift position SHFT is switched from the N to the D. In this procedure, the duty ratio to the electromagnetic valve is decreased at time t 13 and is then gradually increased. The throttle valve opening degree TA starts increasing from time t 12 due to depression of the acceleration pedal. At time t 13 , the throttle opening degree TA is set to the idle throttle opening degree TAecoidl (TAecoidl=0%). In this manner, the hydraulic pressure applied to the clutch C 1 is gradually increased.

At time t 14 , the clutch C 1 stops slipping. Then, the throttle opening degree TA is increased according to the routine of FIG. 7 until the throttle opening degree TA reaches a value of the normal control procedure at time t 16 . If the duty ratio of the electromagnetic valve is not controlled in step S 380 or if the throttle valve opening degree TA is not controlled in step S 410 , the hydraulic pressure applied to the clutch C 1 is suddenly increased as shown by broken line.

FIG. 10 shows a case that is slightly different from the case of FIG. 9 . Specifically, the driver releases the brake pedal but does not press the acceleration pedal in the case of FIG. 10 . If the clutch C 1 is detected to be slipping in this case, the duty ratio of the electromagnetic valve is decreased at time t 22 . Then, the duty ratio is gradually increased. Accordingly, the hydraulic pressure applied to the clutch C 1 is gradually increased.

The above embodiment has the following advantages.

If the hydraulic pressure generated by the hydraulic pressure controller 6 a is insufficient due to, for example, a malfunction in the electric oil pump 36 , a relatively high hydraulic pressure generated by the oil pump of the automatic transmission 6 creates an excessive shock when the clutch C 1 is engaged after the engine 2 is automatically started.

However, in this embodiment, the throttle opening degree TA is set to 0% to minimize the output torque of the engine. Therefore, the output torque of the engine 2 is not suddenly transmitted to the automatic transmission 6 and the devices that are coupled to the automatic transmission 6 . Accordingly, the shock due to engagement of the clutch C 1 is reduced.

When the clutch C 1 stops slipping, the throttle opening degree TA is gradually increased to a value of the normal control procedure. Accordingly, the output torque of the engine 2 is gradually increased. Therefore, the shock when the output torque is restored is reduced.

Further, when engagement of the clutch C 1 is expected to generate a shock, the hydraulic pressure applied to the clutch C 1 is gradually changed from the engagement state from the non-engagement state or from the half engagement state. Therefore, the output torque of the engine 2 is not suddenly transmitted to the automatic transmission 6 of the devices that are coupled to the automatic transmission 6 . Thus, the shock generated when the clutch C 1 is engaged is further reduced.

As in the equations (1) and (2), whether the clutch C 1 is slipping is easily detected based on the turbine speed NCO, the speed NAO of the output shaft 6 b and the gear ratio Gr.

A second embodiment of the present invention will now be described with reference to FIG. 11 . The embodiment of FIG. 11 does not include an electric oil pump. While the automatic stop procedure of an engine 102 is being executed, an accumulator 136 applies hydraulic pressure to a hydraulic pressure controller 106 a . Only the differences from the embodiment of FIGS. 1 to 10 will be discussed.

When the engine 102 is running, an oil pump 106 d of an automatic transmission 106 applies hydraulic pressure to the hydraulic pressure controller 106 a through a check valve 136 a . Therefore, when the engine 102 is running, hydraulic pressure is accumulated in the accumulator 136 . When the engine 102 is automatically stopped, the pressure in the oil pump 106 is lowered. However, the check valve 136 a maintains the pressure in the accumulator 136 . Thus, when the engine 102 is automatically stopped, the engagement of the clutch C 1 is reliably maintained.

If the hydraulic pressure applied to the hydraulic pressure controller 106 a by the accumulator 136 is insufficient, the clutch C 1 slips when the engine 102 is automatically started. At this time, based on the procedures shown in FIGS. 6 and 7, the shock generated by engagement of the clutch C 1 is reliably prevented.

In addition to the advantages of the embodiment of FIGS. 1 to 10 , the embodiment of FIG. 11 has the following advantages.

Since the system of FIG. 11 does not include an electric oil pump, the structure is simplified, which reduces the cost and saves the power of the battery 27 . As a result, the fuel economy is improved. judges that the clutch C 1 is not slipping and temporarily suspends the current routine.

If the outcome of step S 640 is positive, that is, if the shift position SHFT is D, the ECU 38 proceeds to step S 650 . In step S 650 , the ECU 38 judges whether the engine speed NE exceeds a reference speed NE 0 . The reference speed NE 0 is for example 400 rpm to 500 rpm. If the outcome of step S 650 is negative, that is if the engine speed NE is equal to or less 10 than the reference speed NE 0 (NE≧NE 0 ), the ECU 38 judges that the clutch C 1 is not slipping and temporarily suspends the current routine.

If the outcome of step S 650 is positive, that is, if the engine speed NE is greater than the reference speed NE 0 (NE>NE 0 ), the ECU 38 judges that the engine speed NE reached the reference speed NE 0 while the output torque of the engine 2 was being transmitted from the input shaft 6 c to the output shaft 6 b of the automatic transmission 6 after the engine 2 had been automatically started. In step S 660 , the ECU 38 judges whether there is still time until a predetermined period T 0 elapses from when the engine 2 was automatically started. The period T 0 is, for example, 0.5 to 1 seconds. If the outcome of step S 660 is negative, that is, if the reference period T 0 has elapsed from when the engine 2 was automatically started, the ECU 38 judges that the clutch C 1 is not slipping and temporarily suspends the current routine.

If the outcome of step S 660 is positive, that is, if there is still time until the reference period T 0 elapses, the ECU 38 proceeds to step S 670 . In step S 670 , the ECU 38 judges whether the turbine speed NCO, which is detected by the second speed sensor 34 , is greater than a reference speed NCX. At this time, the engine 2 is running after being automatically started and the vehicle is in a non-moving state or substantially in a non-moving state, and the wheels are almost not rotating. If the clutch C 1 is not slipping, the turbine speed NCO is zero or substantially zero. In the embodiment of FIG. 12, the reference speed NCX represents zero or substantially zero of the turbine speed NCO.

If the outcome of step S 670 is negative, that is if the turbine speed NCO is equal to or less than the reference speed NCX (NCO≦NCX), the ECU 38 judges that the clutch C 1 is not slipping and temporarily suspends the current routine. If the outcome of step S 670 is positive, that is, if the turbine speed NCO is greater than the reference speed NCX (NCO>NCX), the ECU 38 proceeds to step S 680 . In step S 680 , the ECU 38 judges that the turbine is not completely held by the wheels and rotating due to slipping of the clutch C 1 . That is, the ECU 38 judges that the clutch C 1 is slipping and temporarily suspends the current routine.

In this manner, the ECU 38 judges whether the clutch C 1 is slipping. The result of the procedure shown in FIG. 12 is referred to in step S 350 of FIG. 6 .

In addition to the advantages of the embodiment shown in FIGS. 1 to 10 , the embodiment of FIG. 12 has the following advantages.

Whether the clutch C 1 is slipping is easily detected by comparing the turbine speed NCO with the reference speed NCX. Also, the second speed sensor 34 , which is used for controlling the automatic transmission 6 , is used for detecting whether the clutch C 1 is slipping. Therefore, whether the clutch C 1 is slipping is detected without using any additional sensor.

A fourth embodiment of the present invention will be described with reference to FIGS. 13 to 14 . The fourth embodiment is the same as the embodiment of FIGS. 1 to 10 except for step S 350 . That is, in the fourth embodiment, the equations (1) and (2) are not used. Instead, the result of the procedure of FIGS. 13, 14 , or the detected engagement state of the clutch C 1 , is referred to in step S 350 . The procedure of FIG. 13 is executed at the same intervals as the procedure of FIG. 12 . Steps S 710 to S 780 of FIG. 13 are the same as steps S 610 to S 680 of FIG. 12 .

If the ECU 38 judges that the clutch C 1 is slipping in step S 780 , the ECU 38 proceeds to step S 790 . In step S 790 , the ECU 38 sets an engagement abnormality flag XCV to ON and temporarily suspends the current routine.

The procedure of FIG. 14 is executed at predetermined intervals. In step S 810 , the ECU 38 judges whether the engine 2 has been automatically started. If the outcome of step S 810 is negative, that is, if the engine 2 has not been automatically started, the ECU 38 temporarily suspends the current routine.

If the outcome of step S 810 is positive, that is, if the engine 2 has been automatically started, the ECU 38 proceeds to step S 820 . In step S 820 , the ECU 38 detects whether the current routine is being executed for the first time after the engine 2 was automatically started. If the outcome of step S 820 is positive, that is, if the current routine is being executed for the first time after the engine 2 was automatically started, the ECU 38 proceeds to step S 830 . In step S 830 , the ECU 38 judges whether the abnormality flag XCF is ON.

If the ECU 38 judges that the clutch C 1 is not slipping in step S 730 in FIG. 13, the abnormality flag XCF remains OFF. Therefore, the outcome of step S 830 of FIG. 14 is negative and the ECU 38 proceeds to step S 840 . In step S 840 , the ECU 38 sets the value of the abnormality flag XCFO of the preceding automatic start procedure to the value of the abnormality flag XCF of the current automatic procedure. That is, the ECU 38 sets the preceding abnormality flag XCFO to OFF. In step S 850 , the ECU 38 sets the abnormality flag XCF to OFF and temporarily suspends the current routine.

Since the subsequent execution of the routine is not the first execution after the engine 2 was automatically started, the outcome of step S 820 is negative, and the ECU 38 temporarily suspends the routine. Therefore, until the engine 2 is automatically started, the procedure of FIG. 14 will not be executed.

If the abnormality flag XCF is ON in step S 790 of FIG. 13, the outcome of step S 830 of FIG. 14 is positive, and the ECU 38 executes step S 860 . In step S 860 , the ECU 38 judges whether the abnormality flag XCFO of the preceding automatic start procedure is ON. That is, the ECU 38 judges whether the clutch C 1 was slipping during the preceding automatic start procedure of the engine 2 .

If the outcome of step S 860 is negative, that is, if the abnormality flag XCFO was set to OFF in the preceding automatic start procedure (in other words, if the clutch C 1 did not slip during the preceding automatic start procedure of the engine 2 ), the ECU 38 proceeds to step S 870 . In step S 870 , the ECU 38 sets a fail counter CFC to one and proceeds to step S 840 . In step S 840 , the ECU 38 sets the value of the abnormality flag XCFO of the preceding automatic start procedure to the value of the abnormality flag XCF of the current automatic start procedure, or to ON, and proceeds to step S 850 . In step S 850 , the ECU 38 sets the abnormality flag XCF to OFF and temporarily suspends the current routine.

If the outcome of step S 860 is positive, that is, if the abnormality flag XCFO of the preceding automatic start procedure is ON (in other words, if the clutch C 1 slipped during the preceding automatic start procedure of the engine 2 ), the ECU 38 proceeds to step S 880 . In step S 880 , the ECU 38 increases the value of the fail counter CFC. In step S 890 , the ECU 38 judges whether the fail counter CFC has exceeded an abnormality determination value nf. In the embodiment of FIG. 13 and 14, the abnormality determination value nf is set, for example, to three.

If the outcome of step S 890 is negative, that is, if an inequality CFC<nf is satisfied, the ECU 38 proceeds to step S 840 . In step S 840 , the ECU 38 sets the value of the abnormality flag XCFO of the preceding automatic start procedure to the current abnormality flag XCF, or to ON. In a subsequent step S 850 , the ECU 38 sets the abnormality flag XCF to OFF and temporarily suspends the routine.

For example, if the clutch C 1 slips every time the engine 2 is automatically started and the abnormality flag XCF is continually set to ON, the outcome of step S 860 is positive. Then, the fail counter CF is increased in step S 880 .

If the outcome of step S 890 is positive, that is, if an inequality CFC≧nf is satisfied, the ECU 38 proceeds to step S 900 . In step S 900 , the ECU 38 judges that the transmission state of the clutch C 1 is abnormal. In a subsequent step S 840 , the ECU 38 sets the value of the abnormality flag XCFO of the preceding automatic start procedure to the value of the current abnormality flag XCF and proceeds to step S 850 . In step S 850 , the ECU 38 sets the abnormality flag to XCF to OFF and temporarily suspends the current routine.

Suppose that the abnormality flag XCF was set to ON in the two preceding automatic start procedures of the engine 2 , since the clutch C 1 slipped, and that the clutch C 1 does not slip in the current automatic start. Since the clutch C 1 is not slipping, the abnormality flag XCF is set to OFF. In this case, the outcome of step S 830 is negative, and the abnormality flag XCFO of the preceding automatic start procedure is set to OFF. Thus, if the clutch C 1 slips in the subsequent automatic start procedure of the engine 2 , the outcome of step S 860 will be negative. In step S 870 , the value of the fail counter CFC is reset to one. Therefore, the engagement state of the power transmission mechanism is judged to be abnormal when the ECU 38 judges that the clutch C 1 is slipping in consecutive automatic start procedures the number of which corresponds to the abnormal determination value nf, which is three in this embodiment.

When the ECU 38 judges that the engagement state of the clutch C 1 is abnormal, an abnormality in the hydraulic pressure controller 6 a , which includes the clutch C 1 , an abnormality in the electric oil pump 36 or the abnormality in the hydraulic system between the controller 6 a and the pump 36 is suspected. Therefore, when the power transmission system is judged to be abnormal, necessary procedures for dealing with the abnormality are performed. For example, a warning lamp of the vehicle, which is located on the dashboard, is lit to warn the driver of the abnormality, and the engine 2 is

A third embodiment of the present invention will now be described with reference to FIG. 12 . The embodiment of FIG. 12 is the same as the embodiment of FIGS. 1 to 10 except for step S 350 . That is, in the embodiment of FIG. 6, the equations (1) and (2) are not used. Instead, the result of the procedure of FIG. 12 for determining the engagement state of the clutch C 1 is referred to in step S 350 . Unless specifically described, the embodiment of FIG. 12 is the same as the embodiment of FIGS. 1 to 10 .

The procedure of FIG. 12 is. executed at predetermined intervals. In step S 110 , running state of the engine 2 is detected. For example, the coolant temperature THW, which is detected by the coolant temperature sensor 66 , the depression state of the acceleration pedal, which is detected by the idle switch 50 , the voltage of the battery 30 , the depression state of the brake pedal, which is detected by the brake switch 64 and the vehicle speed SPD, which is computed based on the detection value of the first speed sensor 32 , are stored in the RAM of the ECU 38 . In step S 610 , the turbine speed NCO, the engine speed NE, the shift position SHFT are stored in the working area of the RAM of the ECU 38 . In step S 620 ,the ECU 38 judges whether the engine 2 is being automatically started. If the outcome of step S 620 is negative, that is, if the engine 2 is not being automatically started, the ECU 38 proceeds to step S 630 . In step S 630 , the ECU 38 judges that the clutch C 1 is not slipping and temporarily suspends the current routine.

If the outcome of step S 620 is positive, that is, if the engine 2 is being automatically started, the ECU 38 proceeds to step S 640 . In step S 640 , the ECU 38 judges whether the shift position SHFT is D. If the outcome of step S 640 is negative, or if the shift position SHFT is not D, the ECU 38 controlled in a limp-home procedure.

In addition to the advantages of the embodiment shown in FIG. 12, the embodiment of FIGS. 13 and 14 has the following advantages.

The clutch C 1 is judged to be slipping when there is not sufficient hydraulic pressure during the automatic start of engine due to a temporary malfunction of the hydraulic controller 6 a or the electric oil pump 36 or due to a temporary malfunction of the clutch C 1 . In this case, however, the clutch C 1 is rarely judged to be slipping in consecutive executions of detection. The clutch C 1 is rarely judged to slip a number of times that corresponds to the abnormality determination value nf (three in this embodiment). Therefore, if the clutch C 1 is judged to slip for more than the number of times set by the value nf, the hydraulic controller 6 a , the electric pump 36 or the clutch C 1 is judged to be abnormal.

Thus, the abnormality of the engagement of the clutch C 1 is reliably detected by the procedure shown in FIG. 14 . Further, when the engagement of the clutch C 1 is detected to be abnormal, the driver is warned and the limp-home control procedure is started. In other words, necessary measures are executed at an early stage.

A fifth embodiment of the present invention will now be described with reference to FIG. 15 . The same reference numerals are given to those steps that are the same as the corresponding steps of the routine of FIG. 6 . In the embodiment of FIG. 15, when the idle switch 50 is on, that is, when the outcome of step S 390 is negative, the duty ratio of the electromagnetic valve is controlled. In this embodiment, when the idle switch 50 is off, the shock of engagement of the clutch C 1 is reduced only by limiting the throttle opening degree TA.

A sixth embodiment of the present invention will now be described with reference to FIG. 16 . The same reference numerals are given to those steps that are the same as the corresponding steps of the routine of FIG. 6 . In the embodiment of FIG. 16, when the clutch C 1 slips, step S 380 is performed, that is, duty ratio of the electromagnetic valve is controlled, and the throttle opening degree TA is not limited. Therefore, shock due to the engagement of the clutch C 1 is reduced only by controlling the hydraulic pressure applied to the automatic transmission 6 , which simplifies the control procedure.

It should be apparent to those skilled in the art that the present invention may be embodied in many other specific forms without departing from the spirit or scope of the invention. Particularly, it should be understood that the invention may be embodied in the following forms.

In the embodiments of FIGS. 1 to 16 , the amount of fuel supplied to the engine 2 may be reduced for reducing the shock of the engagement of the clutch C 1 . For example, in a lean burn engine such as a cylinder injection type gasoline engine or in a diesel engine, the fuel supply amount may be minimized when the clutch C 1 is slipping. In this case, when the clutch C 1 stops slipping, the fuel supply amount is gradually increased to a normal level.

The output torque may be prevented from increasing by prohibiting the target value TAt of the throttle opening TA from increasing. Alternatively, the speed of increase of the target value TAt may be limited so that the target value TAt is increased slowly. Accordingly, the increase of the output torque is limited.

The embodiment of FIGS. 1 to 10 may be applied to an automatic transmission in which an electric oil pump supplies hydraulic pressure to a hydraulic pressure controller not only during automatic stop procedure but also when the engine is running. In this type of automatic transmission, if sufficient electricity cannot be supplied to the electric oil pump due to, for example, a malfunction of the battery after the engine is automatically stopped, a shock may be generated when the engine is automatically started. This is because electricity is suddenly supplied to the electric oil pump from a motor-generator. If applied, the procedure of the embodiment shown in FIGS. 1 to 10 reduces such shock.

In step S 660 of FIG. 12 and in step S 760 of FIG. 13, whether the vehicle speed SPD has exceeded a reference speed value (for example 4 km/h) may be judged. In this case, if the vehicle speed SPD is less than the reference value in steps S 660 , S 760 , the outcome is positive. The speed NAO of the output shaft 6 b of the automatic transmission 6 , which is detected by the first speed sensor 32 , represents the vehicle speed SPD. The speed NAO may be used as the vehicle speed SPD.

The outcome of steps S 660 and S 760 may be positive either when the reference period TO has not elapsed or when the vehicle speed SPD is less than the reference speed. Steps S 660 and S 670 may be more strict. Specifically, the outcome of steps S 660 and S 670 may be positive when the reference period T 0 has not elapsed and the vehicle speed SPD is less than the reference speed.

In step S 680 of FIG. 12 and in step S 780 of FIG. 13, the ECU 38 may compute a cumulative number of rotations of the input shaft 6 c based on the output of the second rotation speed sensor 34 , after the automatic start of the engine 2 is started, and may judge that the clutch C 1 is slipping if the cumulative number of rotation exceeds a reference-number. In this case, the number of rotation is, for example, the cumulative number of e turbine after the engine 2 was automatically started or after the speed NE exceeded the reference speed NE 0 .

In step S 670 of FIG. 12 and in step S 770 of FIG. 13, the ECU 38 may judge whether the equation (2) of the embodiment shown in FIGS. 1 to 10 is satisfied or whether the equation (5), which will be discussed below, is satisfied.

In step S 660 of FIG. 12 or in step S 670 of FIG. 13, the reference period TO may be started when the inequality NE>NEO is satisfied in step S 750 .

The second speed sensor 34 may directly detect the speed of the input shaft 6 c of the automatic transmission 6 .

In step S 350 of FIGS. 6, 12 and 13 , the ECU 38 may judge that the clutch C 1 is slipping if the following equation (4) is satisfied and may judge that the clutch C 1 is slipping when the following equation (5) is satisfied.

NCO≦NAO×Gr+α   (4)

NCO>NAO×Gr+α   (5)

In the equations (4) and (5), the value α represents an acceptable level of the difference between the value detected by the second speed sensor 34 and the value detected by the first speed sensor 32 when the clutch C 1 is not slipping.

The value a may be relatively great. In this case, when the clutch C 1 is substantially completely engaged from a non-engaged state, the outcome of step S 350 in FIG. 6 is negative.

The hydraulic pressure applied to the clutch C 1 , the hydraulic pressure generated by the oil pump 36 or the hydraulic pressure generated by the accumulator 136 may be detected, and when the detected pressure is lower than a reference value, the ECU 38 may judge that the clutch C 1 is not effectively transmitting power.

Therefore, the present examples and embodiments are to be considered as illustrative and not restrictive and the invention is not to be limited to the details given herein, but may be modified within the scope and equivalence of the appended claims.