Shift control apparatus of continuously variable transmission

Abstract: A shift control apparatus outputs a command transmission ratio to a continuously variable transmission (CVT) to control a real transmission ratio of the CVT. The shift control apparatus comprises a shift mode determining section determines whether an actually selected shift mode is an automatic upshift or a power-down upshift (foot-release upshift), on the basis of the result of a previously selected shift mode, a difference between a final objective transmission ratio and a transient objective transmission ratio and a rate of change in the transmission ratio per time. The dynamic characteristic selecting section determines the dynamic characteristic according to the determined shift mode.

Description: The present invention relates to a shift control apparatus of a continuously variable transmission according to the preamble part of the independent claim 1. JP-A- 08074958 and, accordingly, corresponding US 5,695,428 disclose a typical shift control apparatus of a continuously variable transmission (CVT) which apparatus is arranged to compare a basic transmission ratio determined according to an operating condition of a CVT equipped vehicle with a transient controlled objective transmission ratio, in order to determine whether the selected shift is an upshift or a downshift. Further, the conventional shift control apparatus is arranged to determine whether the executed upshift is an automatic upshift or a power-down upshift, by checking a rate of change in a throttle opening TVO of an engine of a vehicle. Herein, the automatic upshift means an upshift executed automatically according to the increase of the vehicle speed, and the power-down upshift means an upshift executed at a time when a foot of a driver is released from an accelerator pedal of the engine. On the basis of the determined shift mode, the conventional shift control apparatus determines a suitable shift speed (a rate of change in the transmission ratio) of the CVT by each of the downshift, the power-down upshift and the automatic upshift, and calculates a transient controlled objective transmission ratio for changing the real transmission ratio to the basic transmission ratio by the determined shift speed. However, JP-A- 08074958 and, accordingly, corresponding US 5,695,428 does not disclose if and how the once determined power-down upshift remains active after the acceleration pedal has been released. It is an objective of the present invention to improve a shift control apparatus of a continuously variable transmission as indicated above so as to accurately execute a shift mode determination between an automatic upshift and a power-down upshift (foot release upshift). According to the present invention, the objective is solved by a shift control apparatus with the features of independent claim 1. Further preferred embodiments of the present invention are laid down in the further subclaims. In the following, the present invention is explained in greater detail by means of several embodiments thereof in conjunction with the accompanying drawings, wherein: Fig. 1 is a block diagram which shows a first embodiment of a shift control apparatus of a continuously variable transmission (CVT) in accordance with the present invention. Fig. 2 is a view for explaining the relationship among a final objective transmission ratio, a transient objective transmission ratio, a command transmission ratio, and a real transmission ratio. Fig. 3 is a graph which shows a control characteristic relating to the objective primary pulley rotation speed of the CVT. Fig. 4 is a flowchart which shows a process executed at a shift mode determining section and a shift control constant determining section of the shift control apparatus. Fig. 5 is a view showing a condition transition view of the shift mode determining section. Fig. 6 is a graph showing a relationship between the shift control constant and the objective ratio deviation for determining a dynamic characteristic of the shift control of the CVT. Figs. 7A to 7E are time charts which show a shift mode determining process of the shift control apparatus according to the present invention. Referring to Figs. 1 to 7, there is shown an embodiment of a shift control apparatus 100 of a continuously variable transmission (CVT) 50 according to the present invention. As shown in Fig. 1, the shift control apparatus 100 according to the present invention is connected to the CVT 50 which produces an infinite number of gear ratios. The CVT 50 of a V belt type comprises, as is commonly known, a primary pulley (input pulley) and a secondary pulley (output pulley) which are arranged to change diameters of their V-shaped grooves. A V-belt is set to the V-shaped grooves of the primary and secondary pulleys to steplessly change a transmission ratio (CVT ratio) corresponding to a gear ratio of a common transmission for a vehicle. The shift control apparatus 100 comprises a command transmission ratio determining apparatus 10 and a transmission control servo apparatus 30. The command transmission ratio determining apparatus 10 receives a signal indicative of a vehicle speed VSP detected by a vehicle speed sensor 21, a signal indicative of a throttle opening TVO detected by a throttle opening sensor 22, and a signal indicative of a rotation speed N pri of the primary pulley detected by a primary rotation speed sensor 23. The command transmission ratio determining apparatus 10 determines a command transmission ratio i PC on the basis of the received signal information. The transmission control servo apparatus 30 executes a feedback control such that a real transmission ratio I PR , which is calculated as a ratio between the primary-pulley rotation speed N pri and a secondary-pulley rotation speed derived from the vehicle speed VSP, is controlled at a command transmission ratio i PC . This feedback control corresponds to a part B in a block diagram of Fig. 2. The command transmission ratio determining apparatus 10 is constituted by an objective primary rotation speed calculating section 11, a secondary rotation speed calculating section 12, a final objective transmission ratio calculating section 13, a transient objective transmission ratio calculating section 14, an objective transmission control constant determining section 15, an objective transmission ratio difference calculating section 16 and the shift mode deciding section 17. The objective primary rotation speed calculating section 11 retrieves an objective primary rotation speed N pri* adapted to a present operating condition by using a preset objective primary rotation speed map such as a map shown in Fig. 3 from the combination of the vehicle speed VSP and the throttle opening TVO. The secondary rotation speed calculating section 12 calculates a secondary rotation speed N sec of the secondary pulley by multiplying a constant to the vehicle speed VSP. The final objective transmission ratio calculating section 13 calculates a final objective transmission ratio i PO by dividing the retrieved objective primary rotation speed N pri* by the secondary rotation speed N sec . The transient objective transmission ratio and command transmission ratio calculating section 14 first calculates a transient objective transmission ratio i PT for realizing the final objective transmission ratio i PO from the equation iPT = [1/(T 0 •S+1)]i PO where T 0 is a time constant, S is a Laplace operator, and [1/(T 0 •S+1)] is a dynamic characteristic corresponding to a part A of Fig. 2. Next, the transient objective transmission ratio and command transmission ratio calculating section 14 calculates a command transmission ratio i PC by multiplying the transient objective transmission, ratio i PT to an inverse system (T T •S+1) which is an inverse system of the dynamic characteristic (T T •S+1) of the transmission control servo apparatus 30 corresponding to the part B of Fig. 2. That is, the transient objective transmission ratio and command transmission ratio calculating section 14 calculates the command transmission ratio i PC from the equation l PC = [(T T •S+1)]l PT . Since the command transmission ratio i PC is obtained from the equation i PC = [(T T •S+1)/(T 0 -S+1)]i PO and the final objective transmission ratio i PO , the real transmission ratio i PR is consequently controlled by the dynamic characteristic iPR = [1/(T 0 •S+1)]i PO with respect to the final objective transmission ratio i PO . Therefore, the real transmission ratio i PR is not affected by the dynamic characteristic [1/(T T •S+1)] and is controlled by the dynamic characteristic affected only by the time constant T 0 . Therefore, the dynamic characteristic of the real transmission ratio i PR can be set freely by the time constant T 0 . Hereinafter, the method for determining the time constant T 0 of the objective transmission control constant will be discussed. The objective transmission ratio difference calculating section 16 calculates an objective transmission ratio difference e iP which is a difference between the final objective transmission ratio i PO and the transient objective transmission ratio i PT (e iP = i PO -i PT ). The shift mode deciding section 17 executes a transmission mode deciding process corresponding to steps S41 to S47 shown in a flowchart of Fig. 4, where it is determined which shift (a downshift or an upshift) is selected, and it is determined which upshift (automatic upshift or power-down upshift) is selected if the upshift is selected. More particularly, at the step S41, it is determined whether or not the objective transmission ratio difference e iP is smaller than a positive shift decision value +D iP . At the step S42, it is determined whether or not the objective transmission ratio difference e iP is smaller than a negative shift decision value -D iP . That is; by the implement of the steps S41 and S42, it is decided as to whether or not the objective transmission ratio difference e iP is out of a range from the negative shift decision value - D iP to the positive shift decision value +D iP. When the determination at the step S41 is affirmative and when the determination at the step S42 is negative, that is, when the objective transmission ratio difference e iP is within a range from the negative shift decision value -D iP to the positive shift decision value +D iP , it is determined that no shift is executed and therefore the routine proceeds to an end so as to maintain the present objective control constant T 0 . When the determination at the step S41 is negative, that is, when it is determined that the downshift is executed, the routine proceeds to a step S51. When the determination at the step S42 is affirmative, that is, when it is determined that the upshift is executed, the routine proceeds to a step S43. In the process of the steps S43 to S47, it is determined as to whether the executed upshift is a power-down upshift or an automatic upshift. More particularly, at the step S43, it is checked whether the shift mode decision result in the previous routine is a downshift, the automatic upshift automatically executed according to the increase of the vehicle speed or the power-down upshift executed when a foot of a driver is released from an accelerator pedal of the engine. When it is determined at the step S43 that the previous decision result of the shift mode is the downshift or the automatic upshift, the routine proceeds to a step S44 wherein it is determined whether a rate ΔN pri* of change in the objective primary rotation speed N pri* is smaller than a power-down upshift decision value K D or not. When the determination at the step S44 is negative, the routine proceeds to a step S47 wherein it is decided that the automatic upshift is executed. When the decision at the step S44 is affirmative, the routine proceeds to a step S45 wherein it is decided that the power-down upshift is executed. When it is determined at the step S43 that the previous decision result as to the selected shift mode is the power-down upshift, the routine proceeds to a step S46 wherein it is determined whether or not the objective transmission ratio difference e iP is greater than an automatic upshift decision value K e . When the determination at the step S46 is affirmative, the routine proceeds to the step S47. When the determination at the step S46 is negative, the routine proceeds to the step S 45. the objective transmission control constant determining section 15 is arranged to determine the time constant T 0 of the objective transmission control constant by executing steps S48 to S52 of Fig. 4. That is, at the step S48, it is checked whether or not the automatic upshift is selected in the present execution or not, that is, which the step S45 or S47 is executed. When it is determined at the step S48 that the power-down upshift is executed, the routine proceeds to a step S49 wherein a transmission control constant map for the power-down upshift embodied in Fig. 6 is selected. Then, the routine proceeds to a step S52 wherein the time constant To is retrieved from the objective transmission ratio difference e iP and the transmission control constant map for the power-down upshift. When it is determined at the step S46 that automatic upshift is executed, the routine proceeds to a step S50 wherein a transmission control constant map for the automatic upshift is selected. Following to the execution at the step S50, the routine proceeds to the step S52 wherein the time constant T 0 is retrieved from the objective transmission ratio difference e iP and the transmission control constant map for the automatic upshift. When it is determined at the step S41 that downshift is executed, the routine proceeds to the step S51 wherein a transmission control constant map for the downshift is selected. Following to the execution at the step S51, the routine proceeds to the step S52 wherein the time constant T 0 is retrieved from the objective transmission ratio difference e iP and the transmission control constant map for the automatic upshift. The time constant T 0 of the shift control determined according to the shift mode is supplied from the objective constant determining section 15 to the transient objective transmission ratio and command transmission ratio calculating section 14. The transient objective transmission ratio and command transmission ratio calculating section 14 obtains the command transmission ratio i PC which is not affected by the dynamic characteristic [1/(T T •S+1)] of the transmission control servo apparatus 30 and is affected by the dynamic characteristic [1/(T 0 •S+1)] determined only by the time constant T 0 , in order to finally obtain the final objective transmission ratio i PO . The obtained command transmission ratio i PC is inputted to the shift control servo apparatus 30. The conditional transition of the shift mode deciding process by the shift mode deciding section 17 is schematically shown by Fig. 5. Herein, a condition VSP=0 in the condition 3 represents that a vehicle starts to move. Since only the automatic upshift is executed during this starting period, it is included in the condition 3 of the automatic upshift. With the thus arranged shift mode decision technique according to the present invention, when the throttle opening TVO is quickly closed by releasing a foot of a driver from the acceleration pedal as shown in Fig. 7A, the shift control apparatus 100 according to the present invention determines that the power-down upshift is executed without determining that the automatic upshift is executed. Although the conventional shift control apparatus has incorrectly determined such a power-down upshift as the automatic upshift, the shift control apparatus 100 according to the present invention correctly determines the upshift shown in Fig. 7A as the power-down upshift as shown in Fig. 7E. When it is determined at the step S44 that the rate ΔN pri* is smaller than the power-down upshift decision value K D or it is determined at the step S46 that the objective transmission ratio difference e iP is smaller than the automatic upshift decision value K e , it is determined at the step S46 that the power-down upshift is executed. Therefore, in case of Fig. 7A, it is determined that the power-down upshift is executed even at a moment t 2 when a foot of the driver operating the engine equipped with the CVT 50 is just released from the acceleration pedal of the engine. Further, the correction determination is held until the moment t 3 when the upshift is completed while avoiding the incorrect determination. Accordingly, as is clear from the rate shown by a dotted line of the transient objective transmission ratio i PT in Fig. 7C, the dynamic characteristics of the upshift control is adapted to the power-down upshift such that the transmission ratio is slowly changed according to the power-down upshift. This solves the conventional problem that the large acceleration and deceleration are generated during such an upshift.

Claims: A shift control apparatus (100) of a continuously variable transmission (50) for outputting a command transmission ratio (i PC ) to the continuously variable transmission (50) to control a real transmission ratio (i PR ) to a final objective transmission ratio (i PO ) by means of a selected dynamic characteristic, comprising: a rate calculating section (13) for calculating a rate of change in an objective transmission input rotation speed (ΔN pri * ) corresponding to the final objective transmission ratio (i PO ); a transient transmission ratio calculating section (14) for calculating a transient transmission ratio (i PT ) which is employed to achieve the final objective transmission ratio (i PO ) using the dynamic characteristic and to determine the command transmission ratio (i PC ); a shift mode determining section (17) for determining whether an actually selected shift mode is an automatic upshift executed according to an increase of a vehicle speed or a power-down upshift executed according to a foot release operation of a driver from an accelerator pedal, on the basis of the rate of change in the objective transmission input rotation speed (ΔN pri *); and a dynamic characteristic selecting section for determining the dynamic characteristic according to the determined shift mode, characterized in that the shift mode is further determined on the result of a previously selected shift mode, and that an objective transmission ratio difference calculating section (16) calculates an objective transmission ratio difference (e iP = i PO - i PT ) between the final objective transmission ratio (i PO ) and the transient objective transmission ratio (i PT ), and wherein the determination of the power-down upshift determined once at the shift mode determining section (17) is maintained until the objective transmission ratio difference (e iP ) becomes greater than a reference value (Ke). A shift control apparatus according to claim 1, characterized by a shift determining section (S41,S42) for determining whether an executed shift is an upshift or a downshift by comparing the objective transmission ratio difference (e iP ) with upper and lower shift decision values (+D iP ,-D iP ). A shift control apparatus according to claim 1 or 2, characterized in that said shift mode determining section is adapted to determine that the power-down upshift (S45) is executed when the previously selected shift (S43) is the automatic upshift and when the rate of change in the objective transmission input rotation speed (ΔN pri *) is smaller than a power-down upshift decision value (K D ), and to determine that the automatic upshift (S47) is executed when the previously selected shift (S43) is the automatic upshift and when the rate of change in the objective transmission input rotation speed (ΔN pri * ) is not smaller than the power-down upshift decision value (K D ). A shift control apparatus according to one of the claims 1 to 3, characterized in that said shift mode determining section is adapted to determine that the automatic upshift (S47) is executed when the previously selected shift (S43) is the power-down upshift and when the objective transmission ratio difference (e iP ) is smaller than an automatic upshift decision value (K e ), and to determine that the power-down upshift (S45) is executed when the previously executed shift (S43) is the power-down upshift and when the objective transmission ratio difference (e iP ) is not smaller than the automatic upshift decision value (K e ). A shift control apparatus according to one of the claims 1 to 4, characterized in that said shift mode determining section is adapted to determine that the power-down upshift (S45) is executed when the previously selected shift (S43) is the downshift and when the rate of change in the objective transmission input rotation speed (ΔN pri * ) is smaller than a power-down upshift decision value (K D ), and to determine that the automatic upshift (S47) is executed when the previously selected shift (S43) is the downshift and when the rate of change in the objective transmission input rotation speed (ΔN pri * ) is not smaller than the power-down upshift decision value (K D ). A shift control apparatus according to one of the claims 1 to 5, characterized in that the dynamic characteristic for achieving the final objective transmission ratio (i PO ) is selected by selecting a time constant (T 0 ), which affects the dynamic characteristic. A shift control apparatus according to claim 6, characterized in that the time constant (T 0 ) is selected from a map selected according to the selected shift mode according the objective transmission ratio difference (e iP ). A shift control apparatus according to one of the claims 1 to 7, characterized in that said continuously variable transmission (50) is a V belt type continuously variable transmission (CVT) connected to an internal combustion engine installed in an automotive vehicle. A shift control apparatus according to claim 8, characterized by a vehicle speed sensor (21) for detecting a vehicle speed and for outputting a vehicle speed indicative signal; a throttle opening sensor (22) for detecting a throttle opening of a throttle valve of the engine and for outputting a throttle opening indicative signal; a primary rotation speed sensor (23) for detecting a rotation speed of a primary pulley of the CVT and for outputting a primary-pulley rotation speed indicative signal (N pri ); a command transmission ratio determining apparatus (10); and a transmission control servo apparatus (30) for controlling the real transmission ratio (i PR ) calculated from the primary-pulley rotation speed indicative signal (N pri ) and the vehicle speed indicative signal by means of a feedback control employing the command transmission ratio (i PC ) as an input and the real transmission ratio (i PR ) as a retransmitted input.

Inventors: ADACHI KAZUTAKA, ASHIZAWA HIROYUKI, OCHIAI TATSUO, ADACHI, KAZUTAKA, ASHIZAWA, HIROYUKI, OCHIAI, TATSUO
Applicants: NISSAN MOTOR, NISSAN MOTOR COMPANY, LIMITED
Application year: 1998
Main classification: F16H61
IPC codes: F16H61, F16H9