Line pressure control arrangement for automatic automotive transmission

Abstract: During non-shift modes of transmission operation, the line pressure is controlled according to a first control schedule. Upon a shift being initiated a second control schedule is used. The use of this schedule is maintained until such time as the ratio of the transmission input shaft rotational speed (17) to the transmission output shaft rotational speed (18) reaches a predetermined limit whereafter a third control schedule is utilized. Control is switched from the third control schedule to the first one upon the expiry of a predetermined period which is timed from the point in time a decision that a shift between gears of the transmission should be implemented.

Description: BACKGROUND OF THE INVENTION Field of the Invention The present invention relates generally to a line pressure control arrangement for automatic automotive transmissions and more specifically to a line pressure control arrangement which enables the appropriate control of line pressure during a plurality of different shifting operations. Description of the Prior Art An automatic transmission Service Manual (publication A261C07) issued in March 1987 relating to the so called RE4RO1A type transmission describes an arrangement which utilizes tabled data for controlling the line pressure during shifting and non-shifting modes of transmission operation. In this arrangement the engine throttle valve opening degree is used to determine the duty cycle of a signal used to control a line pressure control solenoid valve. However, with this arrangement because the line pressure is controlled by a single throttle valve position - line pressure relationship during shifting operations it has been found very difficult to successfully control the line pressuring during all of the various shift possibilities. For example, when the transmission undergoes a power OF upshift with the engine throttle valve held in a given position, and the transmission shifts from first to third (1-3) and the shifts again from third to fourth (3-4), the ratio of the transmission input shaft rotational speed to the transmission output shaft rotational speed undergoes a large change. Accordingly, the line pressure correction must similarly undergo a large change. Further, when the vehicle is coasting with the throttle valve fully closed and the transmission undergoes a power OFF 1-2 upshift, a one-way clutch which is included in the transmission gear train assumes a released position and idles while the engagement level is low and an accumulator which is designed to maintain the line pressure at a reduced level during this particular shift in a manner which attenuates shift shock, induces the problem that following the completion of the shift, the line pressure is induced to undergo a sharp increase and the pressure reducing function of the accumulator is subject to an early termination. This leads to the situation wherein the friction elements to become engaged with a force which is excessive for the instant set of operating conditions. A control system for a transmission according to the preamble of claim 1 is disclosed in DE-A-32 05 767. It is proposed in this document to use the transmission ratio for controlling the gear shift. The transmission ratio is derived from the input rotational speed and the output rotational speed. The line pressure of the hydraulic fluid is controlled in such a way that the transmission ratio during a gear shift is characterized by a predetermined function. SUMMARY OF THE INVENTION It is the object of the present invention to provide a line pressure control system for an automatic transmission which can selectively control the line pressure to appropriate levels during each of the various shifts which occur. This object is solved by a control system for a transmission according to the single claim. The invention is now described in detail with respect to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic drawing showing an automotive power train which is equipped with an embodiment of the present invention; Fig. 2 is flow chart depicting the steps which are executed by a main control routine during the operation of the embodiment of the present invention; Fig. 3 is a flow chart depicting the steps which are executed in accordance with a sub-routine which is run in the main control shown in Fig. 2; Figs. 4A and 4B are charts showing, in terms of engine throttle valve opening and gear shift ratio values g1 and g2, the control characteristics which are used during 1-4 and 1-2 upshifts, respectively; Fig. 5A is a table which shows in terms of throttle opening and duty cycle, a basic line pressure control schedule which is used during before and after a shift control operation is conducted; Figs. 5B and 5C show tables which depict the duty cycle control schedules used during 1-4 upshifts; Figs. 5D and 5E show tables which depict the duty cycle control schedules used during 1-2 upshifts; Fig. 6 is a timing chart which shows the operation induced by the present invention during a 1-4 power ON upshift; and Fig. 7 is a timing chart which shows the operational characteristics induced by the present invention during a power OFF 1-2 upshift. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Fig. 1 shows a power train to which an embodiment of the present invention is applied. In this arrangement an electronically fuel injected internal combustion engine 1 is operatively connected by way of a power train (generally denoted by the numeral 2) with a differential gear 3. Driving wheels 4 are connected to the differential 3. It should be understood that even though Fig. 1 shows a F-R power train (front engine - rear wheel drive) the present invention is not limited to the same and can be applied to FF, MR or four-wheel drive 4WD type arrangements if so desired. The engine control system includes an engine control unit 5 which is supplied inputs from an engine speed sensor 6, a vehicle speed sensor 7, a throttle position sensor 8, and an intake air sensor 9. Based on the inputs of sensors 6 to 9, the control unit 5 which in this instance includes a microprocessor (not show), derives the appropriate injection control pulse width and applies the same to the fuel supply system of the engine. In this embodiment, the power train 2 includes a RE4RO1A type transmission developed by NISSAN MOTOR CO. LTD., the construction and arrangement of which is described in detail in the Service Manual A261CO7 published by the above mentioned company. A torque converter 10 including a lock-up clutch provides an operative connection between the output shaft of the engine and an input shaft 12 of a gear train 11. A transmission output shaft 13 provides a drive connection between the differential or final gear 3 and the transmission. The system includes a shift control unit 14 which also includes a microprocessor. This unit 14 is arranged to issue control signals to a control valve unit 15 which forms part of the transmission. The control valve unit 15 includes three solenoids 15a, 15b and 16. In this embodiment the transmission includes a gear train comprising a plurality of planetary gear units, and associated hydraulically operated clutches and brakes (not shown). The brakes and clutches are operated by the supply of so called "line pressure" PL which is selectively supplied from the control valve unit 15. Depending on the energization of solenoids 14a and 15b, the transmission is conditioned to selectively produce a number of different gear ratios by selectively inducing line pressure PL to be supplied to the appropriate friction elements. In this instant arrangement four forward gear ratios of the transmission can be produced in the manner indicated in the table below. GEAR: FIRST SECOND THIRD FOURTH SOL. 15a: ON OFF OFF ON SOL. 15b: ON ON OFF OFF The third solenoid 16 of the control valve unit 15 is arranged to be operated on a variable duty cycle and to control the level of the line pressure PL. With this arrangement as the duty cycle increases the level of the line pressure is increased. The shift control unit 14 is arranged to receive data inputs NT and NO from rotational speed sensors 17 and 18 respectively. As will be appreciated from the drawings, NT is indicative of the rotational speed of the input shaft 12 of the transmission while NO is indicative of the rotational speed of the transmission output shaft 13. It is worth noting that the output of the sensor 18 can be used additionally as a vehicle speed indicative signal if so desired. This unit 14 further receives data inputs V, TH and Id from the vehicle speed sensor 7, the throttle position sensor 8 and an idle switch 19. Programs of the nature depicted in the flow charts of Figs. 2 and 3 are run in the shift control unit microprocessor in order to derive the appropriate control signals. In this embodiment the main control routine shown in Fig. 2 is arranged to be run at 10 msec intervals (by way of example). Fig. 2 depicts the main control routine in flow chart form. At steps 21 and 22 of this routine, the outputs of sensors 8, 17 and 18 are sampled and the instant values of TH, NT and NO are read and set in memory for further processing. At step 23 the ratio g of the transmission input shaft speed to the transmission output shaft speed is derived. Following this, in step 24 the output of the vehicle speed sensor 7 is sampled and the instant value of V read into memory. This data is then used in combination with the instant throttle valve position TH to determine, from shift pattern table data, the most appropriate gear (i.e. speed gear ratio) for the transmission to be conditioned to produce. This is logged as a target gear. At step 25 the instant gear the transmission is conditioned to produce is compared with the target one. If there is no difference, the program flows to step 26 wherein a command which maintains the current energization status of the solenoids 15a and 15b is issued and the routine then proceeds to steps 34 and 35 where energization signals are outputted to the solenoids and a line pressure sub-routine is performed. Note that this just mentioned sub-routine will be described later in connection with the flow chart shown in Fig. 3. However, if at step 25 it is discovered that there is a difference between the target gear and current one the transmission is conditioned to produce, then the routine flows to step 27 wherein the type of shift which must be implemented to achieve the target value is determined. By way of example, it may be found that a 1-4 upshift is required. Next, at step 27 the instant status of a shift flag F is determined. If the value of this shift flag is not "1" then the routine flows across to step 29 where the value is set to 1 and a timer count T set to zero. Following this, the program loops to step 31. On the other hand, if the outcome of the enquiry conducted at step 28 is affirmative, then at step 30 the count of timer T is incrementally increased. Step 31 is arranged to check the count of timer T and to determine if a predetermined period of time has elapsed or not. While this period has not elapsed the routine flows to steps 32 and 33. In step 32 the gear ratio data necessary to implement the shift which is indicated as being necessary in step 27 is read out of memory. For example, if a 1-4 upshift is indicated as being necessary the data such as that depicted in Fig. 4A is read out of memory and installed ready for use. At step 33 the instant value of g is compared with the values of g1 and g2 of the data prepared in step 32. For example, if the instant value of g is between g1 and g2 then the solenoids are de-energized in step 34 (see the 1-4 power ON upshift timing chart - Fig. 6). Until timer T has reached the To count, the routine continues to flow through steps 32 to 34. Accordingly, as each run is made the instant value of g is updated and it becoming equal to or less than g2. At this time the solenoid conditioning is revised. For example in the case of a 1-4 upshift with power "on", solenoid 15a is re-energized. This particular operation changes the shifting of the transmission from a 1-3 to a 3-4 shift in the manner shown in Fig. 6. When timer T has reached the count To indicative of the above mentioned period having elapsed (step 31), the flow of the routine changes and it then flows across to step 36 where the post shift decision solenoid energization settings, which are necessary to condition the transmission to produce the target gear, are issued. For further information relating to the type of operations which are performed in the above mentioned steps 32 and 33 reference can had to US-A-4,970,916. Fig. 3 shows a flow chart which depicts the steps performed by the line pressure control sub-routine which is run at step 35. As will be appreciated the first step of this routine is such as to determine the instant status of the shift flag F. In the event that the shift flag has not be set to "1" then the routine flows across to step 42 where Table 0 is read out and set as the instant line pressure control table. The appropriate duty cycle to be applied to solenoid 16 is then looked up. Following this, the routine flows to step 43 wherein the appropriate control signal is applied to the line pressure control solenoid. It will be noted that while shift flag F is not set to "1" the transmission is indicated as operating in a non-shift mode. Under these modes of operation Table 0 provides the appropriate line pressure control characteristics. On the other hand, if the shift flag F has been set to "1" indicating that a shift mode has been entered, then the program flows to step 44. In this step the instant g1 and g2 values which will be used for the solenoid energization control are established on the basis of the type of shift which is indicated as being necessary, the throttle position TH and the status of the idle switch. These values are set in memory ready for further processing. It will be noted that in the case of upshifts g1 > g2 while in the case of downshifts, the reverse situation occurs viz., g2 > g1. Next, in step 45, the type of shift which is apt to be induced by the instant set of operating conditions is screened in a manner which enables it to be determined if the shift will be an upshift or not. In the case of an affirmative outcome, the routine proceeds to step 46 wherein it is determined if the instant g value is less than or equal to g1. In the case of an affirmative outcome the routine proceeds to step 47 wherein the instant value of g is compared with g2 in a manner which determines if it is less than or equal to the same. In the case of a negative outcome in step 46 the routine flows to step 42, it being indicated that the system is operating in a quasi non-shift mode and induces the use of Table 0 for the line pressure control. On the other hand, in the case of a negative outcome in the enquiry conducted in step 45 the routine goes to step 48 where the instant status of the idle switch is determined. In the case the switch is ON the routine proceeds to step 50 wherein a duty cycle deemed suitable for the instant set of circumstances is established using tabled data entitled DATA 1. Following this the routine proceeds to step 43 wherein the duty cycle selected is implemented. In this embodiment, the two sets of data (DATA 1, and DATA 2 of the nature set forth below in Table 2) are stored in ROM. DATA 1 DATA 2 SHIFT DUTY SHIFT DUTY 1-2 50% 1-2 95% 1-4 40% 1-4 50% In the case the outcome of the enquiry conducted at step 48 reveals that the idle switch is not ON then at step 49 table 1 for the instant shift is set as the line pressure duty cycle control table, and the appropriate duty for the instant throttle opening degree TH (viz., the value recorded in step 21) is determined by look-up. In the case the routine flows to step 51, the idle switch status is checked. In the event that it is not ON, the routine flows to step 52 where the Table 2 data for the instant type of shift (viz., 1-2 or 1-4) is set as the duty cycle for the signal by which the line pressure solenoid 16 is operated. The appropriate duty cycle is then determined using the instant value of TH. However, in the event that the idle switch is found to be ON, then at step 53 DATA 2 is used to set the line pressure control duty cycle. Steps 54 to 61 are essentially similar to steps 45 to 53 and are arranged to screen the instant value of g against g1 and g2 as set in step 44, and to induce the use of TABLES 1 or 2 of the use of DATA 1 or 2 as the situation demands. The control provided by the instant embodiment of the invention is deemed to be clear from the timing charts of Figs. 6 and 7. As will be noted at the bottom of these charts, Table 0 is used when the system is not undergoing a shift, while once in a shift mode, the appropriate Table 1 data is used until such time as the g value reaches the g2 level. Following this event the appropriate Table 2 data is used to control the level of the line pressure. The effect of this type of control is demonstrated by the trace PL which forms part of the "hydraulic pressure" section of the charts. In the case of the 1-2 power OFF upshift shown in Fig. 7, until the value of g falls to that of g2 the line pressure control continues to be determined by the schedule defined in Table 0 and remains at the same level as that used during non-shift modes of transmission operation during the "standby" period, as no change in the shift control solenoids 15a and 15b is induced during the same. The time period for which timer T is arranged to count is fixed at a single value which is selected to correspond to the period which is required for any given shift be completed. As will be noted, in the case of the 1-4 shift shown in Fig. 6, the pressures in the various chambers of the friction elements have already finished increasing when time To is reached. On the other hand, in the case of a 1-2 shift the pressure in the second speed apply chamber 2A is still increasing at the time when timer T completes its count. However, as will be noted the pressure is sufficiently high as to ensure that sufficient engagement of the friction element in question, is produced (note that this is a power OFF type shift). As will be appreciated from the above, Table 0 is designed for fully engaged friction element operation (viz., non-transitory or non-shift modes) and arranged to produce the appropriate engagement pressure level with respect to the load being applied (indicated by the engine throttle valve setting). Although the timing charts show only two of the number of different shifts which are possible and are restricted to upshifts, it will be apparent to those skilled in the art to which the present invention pertains, that a similar type line pressure control can be implemented during downshifts in addition to upshifts and that, in light of the above disclosure, the necessary tables and programs required could be compiled without undue experimentation.

Claims: A control system for a transmission which includes: a transmission input shaft rotational speed sensor (17); a transmission output shaft rotational speed sensor (18); control valve means (15) which controls the supply of hydraulic fluid to the friction elements of the transmission gear train; an electronically controlled line pressure control device (16); transmission control circuitry (14) which receives inputs (NT, No) from said transmission input shaft rotational speed sensor (17) and a transmission output shaft rotational speed sensor (18) and develops a NT/No ratio; and a memory which is included in the transmission control circuitry in which line pressure control data is stored, said memory containing a first memorized table (Table 0) which is used to determine the line pressure level during non-shifting modes of transmission operation and a plurality of memorized second and third tables (Table 1, Table 2) which are used to control the line pressure during different shifts, said memorized data being constantly used to control the level of line pressure during both shift and non-shifting modes of transmission operation, and means for issuing electronic control signals to the control valve means (15), characterized in that said memory control valve means (15) contains first and second solenoids (15a,15b); in that the second table (Table 1) is used from the time the shift is initiated and the third table (Table 2) is used from the time one of the solenoids (15a,15b) changes its energization status, until a predetermined time from the shift initiation has lapsed, and in that after the predetermined time has lapsed, the first table (Table 0) is used again to control non-shifting line pressure level.

Inventors: NARITA YASUSHI, NARITA, YASUSHI
Applicants: NISSAN MOTOR, NISSAN MOTOR CO., LTD.
Application year: 1989
Main classification: B60K41
IPC codes: F16H61