JP2010169125A - Shift control device for vehicular automatic transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a shift control device for a vehicular automatic transmission, having improved pre-shift predicting accuracy. <P>SOLUTION: When achieving a predetermined shift stage, a transmission control unit 100 uses at least one parameter out of the rotating speed of a transmission output shaft, a vehicle speed and the footing amount of an accelerator pedal for predicting the next shift stage. It performs pre-shift control to selectively connect a transmission input shaft and the transmission output shaft to each other via a clutch, not used for achieving a current shift stage, with a predetermined synchronous engagement mechanism to hold them at the predetermined shift stage. When a driver operates a turn indicator to show his right-turn or left-turn intent, the transmission control unit 100 performs pre-shift control to operate the predetermined synchronous engagement mechanism to hold them on a down-shift side beyond the current shift stage. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a control device for an automatic transmission for a vehicle, and more particularly to a shift control device for an automatic transmission for a vehicle suitable for controlling a gear-type transmission used in an automobile.

  Recently, an automated manual transmission (hereinafter referred to as “automatic transmission”) is a system that automates the operation of a clutch as a friction mechanism and the operation of a synchronous meshing mechanism as a gear selection mechanism using a gear-type transmission used in a manual transmission. MT ") has been developed. In automatic MT, when shifting is started, a clutch for transmitting and shutting off engine torque as a driving force source is released, the synchronous meshing mechanism is switched, and then the clutch is engaged again.

  There is also known a twin clutch type automatic MT in which two clutches for transmitting input torque to the transmission are provided, and driving torque is alternately transmitted by the two clutches (see, for example, Patent Document 1 and Patent Document 2). ). In this twin clutch type automatic MT, when shifting is started, the clutch of the next shift stage is gradually engaged while gradually releasing the clutch that was transmitting torque before shifting, and the driving torque is then shifted before shifting. By changing from the gear ratio equivalent to the gear ratio after shifting, the driving torque can be interrupted and smooth shifting can be performed.

  In the twin clutch type automatic MT, in order to shorten the shift time to the next stage, the next shift stage is predicted when the predetermined shift stage is achieved, and the current shift stage is achieved. A so-called pre-shift control is known in which a transmission input shaft and a transmission output shaft to which an unused clutch is connected are selectively connected by a synchronous meshing mechanism so as to wait at a predetermined gear position. (For example, see Patent Document 3 and Patent Document 4).

JP 2000-234654 A JP 2001-295898 A Japanese Patent Laid-Open No. 10-318361 JP 2003-269592 A

  In the twin clutch type automatic MT, if the standby gear position of the pre-shift control to be standby based on the prediction result matches the target gear position when the next shift is started, torque is transmitted before the start of the shift. It is only necessary to gradually engage the clutch of the next shift stage while gradually releasing the clutch. However, if they do not match, switch the synchronous meshing mechanism, engage the gears that make up the desired gear, and then gradually release the clutch that was transmitting torque before starting the gear shift. It is necessary to perform an operation of gradually engaging the gear clutch. As described above, since the prediction accuracy of the preshift greatly affects the responsiveness from the start of the shift to the completion of the shift, it is important to improve the prediction accuracy.

  An object of the present invention is to provide a shift control device for a vehicular automatic transmission with improved preshift prediction accuracy.

(1) In order to achieve the above object, the present invention provides a plurality of friction transmission mechanisms that transmit and block power of a driving force source, and a plurality of transmission input shafts respectively coupled to the plurality of friction transmission mechanisms. The plurality of transmission input shafts and the transmission output shaft are used for controlling an automatic transmission having a plurality of gear trains selectively connected by a selection operation of a plurality of synchronous mesh mechanisms, The transmission input shaft to which the friction transmission mechanism is connected and the transmission output shaft are connected via a gear train, and one of the friction transmission mechanisms is engaged and the other friction transmission mechanism is released. When a desired shift speed is achieved and a predetermined shift speed is achieved, at least one parameter of the rotation speed of the transmission output shaft, the vehicle speed, or the depression amount of the accelerator pedal is used. Next gear The transmission input shaft to which the friction transmission mechanism that is not used for achieving the current gear stage is coupled is operated by operating the predetermined synchronous meshing mechanism based on the prediction result. A shift control device for an automatic transmission for a vehicle that performs pre-shift control in which the output shaft of the transmission is connected via a predetermined gear train and waits, and a direction indicator that indicates a driver's intention to turn right or turn left When the above operation is performed, control means for operating pre-determined synchronous meshing mechanism and performing pre-shift control to make it stand by on the downshift side from the current gear position is provided.
With this configuration, the preshift prediction accuracy can be improved.

  (2) In the above (1), preferably, the control means operates the predetermined synchronous meshing mechanism when the direction indicator is operated, and stands by on the downshift side from the current gear position. If the shift operation is not started in a period from when the direction indicator is operated until a predetermined time elapses, the rotation speed of the transmission output shaft, the vehicle speed, or the accelerator pedal The transmission to which the friction transmission mechanism that is not used to achieve the current shift speed is connected based on a prediction result of the next shift speed using at least one parameter of the depression amount Pre-shift control is performed in which the input shaft and the transmission output shaft are connected to each other via a predetermined gear train and are put on standby.

  (3) In the above (1), preferably, the control means operates the predetermined synchronous meshing mechanism after a predetermined delay time has elapsed since the operation of the direction indicator, and performs a current shift. The pre-shift control is performed so that it waits on the downshift side from the stage.

  (4) In the above (3), preferably, the control means makes the delay time different depending on whether the operation of the direction indicator is a right turn intention or a left turn intention.

  (5) In the above (3), preferably, the control means changes the delay time according to a vehicle speed.

  According to the present invention, the accuracy of preshift prediction can be improved.

Hereinafter, the configuration and operation of a shift control apparatus for a dual-use automatic transmission according to an embodiment of the present invention will be described with reference to FIGS.
First, a first configuration example of the vehicle automatic transmission and the control device according to the present embodiment will be described with reference to FIG.

  FIG. 1 is a skeleton diagram of a system configuration example showing the configuration of an automatic transmission for a vehicle and a control device according to an embodiment of the present invention.

  An engine speed sensor (not shown) that measures the speed of the engine 7, an electronically controlled throttle (not shown) that adjusts the engine torque, and a fuel amount that matches the intake air amount are injected into the engine 7 that is a driving force source. A fuel injection device (not shown) is provided. The engine control unit 101 can control the torque of the engine 7 with high accuracy by operating the intake air amount, the fuel amount, the fuel injection timing, the ignition timing, and the like. Fuel injection devices include an intake port injection method in which fuel is injected into an intake port or an in-cylinder injection method in which fuel is directly injected into a cylinder. The operating range required for the engine (determined by engine torque and engine speed) It is advantageous to use an engine of a type that can reduce fuel consumption and has good exhaust performance. As a driving force source, not only a gasoline engine but also a diesel engine, a natural gas engine, an electric motor, or the like may be used.

  The automatic transmission 50 includes a first clutch 8 and a second clutch 9, which are friction transmission mechanisms, and a first input shaft 41, a second input shaft 42, an output shaft 43, a first drive gear 1, and a second drive gear. 2, third drive gear 3, fourth drive gear 4, fifth drive gear 5, reverse drive gear (not shown), first driven gear 11, second driven gear 12, third driven gear 13, fourth driven gear 14, fifth driven gear 15, reverse drive gear (not shown), first synchronous mesh mechanism 21, second synchronous mesh mechanism 22, third synchronous mesh mechanism 23, rotation sensor 31, rotation sensor 32, rotation sensor 33 is provided.

  By engaging and releasing the first clutch 8, the torque of the engine 7 can be transmitted to and cut off from the first input shaft 41. Further, by engaging and releasing the second clutch 9, the torque of the engine 7 can be transmitted to and shut off from the second input shaft 42. In this example, the first clutch 8 and the second clutch 9 are so-called dry single-plate clutches.

  The second input shaft 42 is hollow, and the first input shaft 41 passes through the hollow portion of the second input shaft 42 and can be moved relative to the second input shaft 42 in the rotational direction. ing.

  A first drive gear 1, a third drive gear 3, a fifth drive gear 5, and a reverse drive gear (not shown) are fixed to the second input shaft 42. The second input shaft 42 is rotatable with respect to the first input shaft 1241. Further, the second drive gear 2 and the fourth drive gear 4 are fixed to the first input shaft 41. The first input shaft 41 is configured to be capable of relative movement in the rotational direction with respect to the second input shaft 42.

  A rotation sensor 31 is provided as means for detecting the rotation speed of the first input shaft 41. A rotation sensor 32 is provided as means for detecting the rotation speed of the second input shaft 42.

  On the other hand, the output shaft 43 is provided with a first driven gear 11, a second driven gear 12, a third driven gear 13, a fourth driven gear 14, a fifth driven gear 15, and a reverse driven gear (not shown). . The first driven gear 11, the second driven gear 12, the third driven gear 13, the fourth driven gear 14, the fifth driven gear 15, and the reverse driven gear (not shown) are provided to be rotatable with respect to the output shaft 43. ing.

  A rotation sensor 33 is provided as means for detecting the rotation speed of the output shaft 43.

  Among these gears, the first drive gear 1 and the first driven gear 11 mesh with the second drive gear 2 and the second driven gear 12, respectively. Further, the third drive gear 3 and the third driven gear 13 are engaged with the fourth drive gear 4 and the fourth driven gear 14, respectively. Further, the fifth drive gear 5 and the fifth driven gear 15 are engaged with each other. A reverse drive gear (not shown), an idler gear (not shown), and a reverse driven gear (not shown) are engaged with each other.

  Further, between the first driven gear 11 and the third driven gear 13, the first synchronous gear 11 is engaged with the output shaft 43, or the third driven gear 13 is engaged with the output shaft 43. A meshing mechanism 21 is provided.

  Further, between the second driven gear 12 and the fourth driven gear 14, the third drive gear 12 is engaged with the output shaft 43, or the fourth driven gear 14 is engaged with the output shaft 43. A meshing mechanism 23 is provided.

  Further, the fifth driven gear 15 is provided with a second synchronous meshing mechanism 22 that engages the fifth driven gear 15 with the output shaft 43.

  A pressure plate (not shown) provided in the first clutch 8 is controlled by the transmission control unit 100 by controlling a current of a first clutch motor 71b (not shown) which is an electric motor provided in the first clutch actuator 71. No) and the transmission torque of the first clutch 8 is controlled. The first clutch actuator 71 is provided with a position sensor 71 a (not shown) that measures the stroke position of the first clutch 8.

  The transmission control unit 100 controls the current of a second clutch motor 72b (not shown), which is an electric motor provided in the second clutch actuator 72, so that the pressure plate provided in the second clutch 9 is controlled. (Not shown) is controlled to control the transmission torque of the second clutch 9. The second clutch actuator 72 is provided with a position sensor 72a (not shown) for measuring the stroke position of the second clutch 9.

  In addition, in order to operate the first clutch 8 and the second clutch 9, in this example, it is configured as an electric operating mechanism using a so-called DC motor, but it is configured using a so-called DC brushless motor or an AC motor. Alternatively, the clutch may be operated by a hydraulic mechanism using an electromagnetic flow control valve, or may be configured by using another mechanism for controlling the first clutch 8 and the second clutch 9. is there.

  The transmission control unit 100 controls the current of a first shift motor (first shift motor 73b in FIG. 2), which is an electric motor provided in the shift actuator 73, to thereby change the current through a shift fork (not shown). By controlling the position or load of the first synchronous meshing mechanism 21 and engaging with the first driven gear 11 or the third driven gear 13, the rotational torque of the second input shaft 42 is changed to the first synchronous meshing mechanism 21. Can be transmitted to the output shaft 43. The shift actuator 73 is provided with a sleeve position sensor (sleeve position sensor 73a in FIG. 2) for measuring the stroke position of the first synchronous meshing mechanism 21.

  Further, the transmission control unit 100 controls the current of a second shift motor (second shift motor 74b in FIG. 2), which is an electric motor provided in the shift actuator 74, so that a shift fork (not shown) is used. By controlling the position or load of the second synchronous meshing mechanism 22 and engaging with the fifth driven gear 15, the rotational torque of the second input shaft 42 is output via the second synchronous meshing mechanism 22 to the output shaft. 43 can be transmitted. The shift actuator 74 is provided with a sleeve position sensor (sleeve position sensor 74a in FIG. 2) for measuring the stroke position of the second synchronous meshing mechanism 22.

  Further, the transmission control unit 100 controls the current of a third shift motor (third shift motor 75b in FIG. 2), which is an electric motor provided in the shift actuator 75, so that a shift fork (not shown) is used. By controlling the position or load of the third synchronous mesh mechanism 23 and engaging with the second driven gear 12 or the fourth driven gear 14, the rotational torque of the first input shaft 41 is adjusted to the third synchronous mesh. It can be transmitted to the output shaft 43 via the mechanism 23. The shift actuator 75 is provided with a sleeve position sensor (sleeve position sensor 75a in FIG. 2) for measuring the stroke position of the third synchronous meshing mechanism 23.

  In addition, in order to operate the 1st synchronous meshing mechanism 21, the 2nd synchronous meshing mechanism 22, and the 3rd synchronous meshing mechanism 23, in this example, it comprises as what is called an electrically operated mechanism using a DC motor. The so-called DC brushless motor or AC motor may be used, or the synchronous meshing mechanism may be operated by a hydraulic mechanism using an electromagnetic pressure control valve and a hydraulic piston. It is also possible to use other mechanisms for controlling the main mechanism 21, the second synchronization meshing mechanism 22, and the third synchronization meshing mechanism 23.

  Thus, from the first drive gear 1, the second drive gear 2, the third drive gear 3, the fourth drive gear 4, and the fifth drive gear 5, the first driven gear 11, the second driven gear 12, and the third driven gear. 13, the rotational torque of the transmission input shaft 41 transmitted to the transmission output shaft 43 via the fourth driven gear 14 and the fifth driven gear 15 is a differential gear (not shown) connected to the transmission output shaft 43. To the axle (not shown).

  In addition, from the lever device 106, a range position signal indicating a shift lever position (P range, R range, N range, D range, M range that enables a shift operation by the driver), and an up switch signal (by a driver operation) Upshift command signal) and downswitch signal (downshift command signal) are input to the transmission control unit 100.

  In addition, a right turn intention display signal and a left turn intention display signal by a driver's operation are input to the transmission control unit 100 from the direction indicator 107. A right turn and left turn intention display signal is input to the transmission control unit 100 as a flashing signal, and a so-called hazard signal in which the right turn intention display signal and the left turn intention display signal flash simultaneously is input to the transmission control unit 100 as both signals flash simultaneously. input.

  Further, the transmission control unit 100 and the engine control unit 101 transmit and receive information to and from each other through the communication unit 103.

  The shift control unit 100 controls the shift actuator 73 to engage the first synchronous meshing mechanism 21 and the first driven gear 11, and the transmission control unit 100 controls the second clutch actuator 72 to control the second clutch 9. Is engaged in the first speed stage.

  The transmission control unit 100 controls the shift actuator 75 to mesh the third synchronous meshing mechanism 23 and the second driven gear 12, and the transmission control unit 100 controls the first clutch actuator 71 to control the first clutch 8. Is engaged to achieve the second speed traveling.

  The shift control unit 100 controls the shift actuator 73 to engage the first synchronous meshing mechanism 21 and the third driven gear 13, and the transmission control unit 100 controls the second clutch actuator 72 to control the second clutch 9. Is engaged in the third speed stage.

  The shift control unit 100 controls the shift actuator 75 to engage the third synchronous meshing mechanism 23 and the fourth driven gear 14, and the transmission control unit 100 controls the first clutch actuator 71 to control the first clutch 8. Is engaged in the fourth speed stage.

  The transmission control unit 100 controls the shift actuator 74 to mesh the second synchronous meshing mechanism 22 and the fifth driven gear 15, and the transmission control unit 100 controls the second clutch actuator 72 to control the second clutch 9. Is engaged in the fifth gear.

  The shift actuator 74 is controlled by the transmission control unit 100, the second synchronous meshing mechanism 22 and the reverse driven gear (not shown) are meshed, and the second clutch actuator 72 is controlled by the transmission control unit 100 to be the second. When the clutch 9 is engaged, reverse gear traveling is performed.

  Here, for example, in the first speed start from the neutral state, the shift control unit 73 is controlled by the transmission control unit 100, and the transmission control unit is further moved from the state where the first synchronous meshing mechanism 21 and the first driven gear 11 are meshed. This is done by controlling the second clutch actuator 72 by 100 and gradually engaging the second clutch 9.

  Next, the input / output signal relationship between the transmission control unit 100 and the engine control unit 101 in the control apparatus for an automatic transmission for a vehicle according to the present embodiment will be described with reference to FIG.

  FIG. 2 is a block diagram showing an input / output signal relationship between the transmission control unit and the engine control unit in the control device for an automatic transmission for a vehicle according to an embodiment of the present invention.

  The transmission control unit 100 is configured as a control unit including an input unit 100i, an output unit 100o, and a computer 100c. Similarly, the engine control unit 101 is also configured as a control unit including an input unit 101i, an output unit 101o, and a computer 101c.

  When the engine torque command value TTe is transmitted from the transmission control unit 100 to the engine control unit 101 using the communication means 103, the engine control unit 101 takes in the intake air of the engine 7 so as to realize the engine torque command value TTe. Amount, fuel amount, fuel injection timing, ignition timing, etc. (not shown) are controlled. The engine control unit 101 includes engine torque detection means (not shown) that serves as input torque to the transmission. The engine control unit 101 rotates the engine speed Ne and the engine torque generated by the engine 7. Te is detected and transmitted to the transmission control unit 100 using the communication means 103. The engine torque detection means may be a torque sensor, or may be an estimation means based on engine parameters such as the injector injection pulse width, the pressure in the intake pipe and the engine speed.

  The transmission control unit 100 receives the first input shaft rotation speed NiA, the second input shaft rotation speed NiB, and the output shaft rotation speed No from the rotation sensor 31, the rotation sensor 32, and the rotation sensor 33, respectively. Further, the transmission control unit 100 receives from the lever device 106 a range position signal RngPos indicating a shift lever position (P range, R range, N range, D range, M range enabling a driver to perform a shift operation). The up switch signal UpSw (upshift command signal) and the down switch signal DnSw (downshift command signal) by the driver's operation are input. The transmission control unit 100 receives a right turn intention display signal Rturn and a left turn intention display signal Lturn by a driver's operation from the direction indicator 107, and the accelerator pedal depression amount Aps from the accelerator opening sensor 201. An ON / OFF signal Brk from the brake switch 202 for detecting whether or not the brake is depressed is input.

  Here, the right turn intention display signal Rturn and the left turn intention display signal Lturn are configured as ON / OFF signals for blinking the right direction indicator lamp and the left direction indicator lamp, respectively, but are in contact with the operation direction of the direction indicator. It may be configured as a continuous signal such as a switch provided with, or may be configured using another mechanism for the transmission control unit 100 to identify the operation of the direction indicator.

  Further, the lubricating oil temperature TEMPlub is input to the transmission control unit 100 from an oil temperature sensor 203 that measures the temperature of the lubricating oil inside the transmission 50.

  The transmission control unit 100 includes a first clutch position sensor 71a that measures the stroke position of the first clutch 8 and a second clutch position sensor 72a that measures the stroke position of the second clutch 9, respectively. RPcl1 and second clutch position RPcl2 are input.

  In addition, the transmission control unit 100 includes a first synchronization mesh mechanism 21, a second synchronization mesh mechanism 22, a third synchronization mesh from the sleeve 1 position sensor 61a, the sleeve 2 position sensor 62a, and the sleeve 3 position sensor 63a. A sleeve 1 position RPslv1, a sleeve 2 position RPslv2, and a sleeve 3 position RPslv3 indicating the stroke positions of the mechanism 23 are input.

  The transmission control unit 100 is provided with a so-called H-bridge circuit (not shown) as a drive circuit for driving the DC motor, and applies the current and current direction of the DC motor to the DC motor by so-called PWM control. Control is performed by adjusting the voltage at the two terminals. The transmission control unit 100 is provided with a current detection circuit (not shown), and controls the current of each motor by changing the voltage output so that the current of each DC motor follows the target current. It has become.

  The transmission control unit 100 sets a target transmission torque Tcl of the first clutch 8 to achieve a desired first clutch transmission torque, sets a target position for realizing the target transmission torque Tcl, The target current and the direction of current for realizing the above are calculated, and by adjusting the voltages V1_cl1 and V2_cl1 applied to the first clutch motor 71b so as to realize the calculated current and current direction, the first clutch motor 71b The current is controlled, and the stroke position of the first clutch 8 is adjusted to engage and release the first clutch 8.

  Further, the transmission control unit 100 sets a target transmission torque Tclb of the second clutch 9 in order to realize a desired second clutch transmission torque, sets a target position for realizing the target transmission torque Tclb, By calculating a target current for realizing the target position and adjusting the voltages V1_cl2 and V2_cl2 applied to the second clutch motor 72b so as to realize the calculated current, the current of the second clutch motor 72b is controlled. The second clutch 9 is engaged and released by adjusting the stroke position of the second clutch 9.

  Further, the transmission control unit 100 adjusts the voltages V1_sft1 and V2_sft1 applied to the first shift motor 73b in order to realize a desired position of the first synchronous meshing mechanism 21, so that the first shift motor 73b The current is controlled, and the first synchronous meshing mechanism 21 is engaged and released.

  Further, the transmission control unit 100 adjusts the voltages V1_sft2 and V2_sft2 applied to the second shift motor 74b in order to realize a desired position of the second synchronous meshing mechanism 22, so that the second shift motor 74b The current is controlled, and the second synchronous meshing mechanism 22 is engaged and released.

  Further, the transmission control unit 100 adjusts the voltages V1_sft3 and V2_sft3 applied to the third shift motor 75b in order to realize a desired position of the third synchronous mesh mechanism 23, whereby the third shift motor 75b The current is controlled, and the third synchronous meshing mechanism 23 is engaged and released.

  For example, when the driver depresses the accelerator pedal with the shift range set to the D range or the like, the transmission control unit 100 determines that the driver is willing to start and accelerate. Further, the transmission control unit 100 determines that the driver intends to decelerate and stop when the driver depresses the brake pedal. The transmission control unit 100 releases the third synchronous mesh mechanism 21, the second synchronous mesh mechanism 22, the second synchronous mesh mechanism so as to release / engage a desired synchronous mesh mechanism so as to realize the intention of the driver. The target positions of the three synchronous meshing mechanism 23 are set, and the voltages V1_sft1, V2_sft1, the voltages V1_sft2, V2_sft2, the third shift applied to the second shift motor 74b are applied to the first shift motor 73b so as to realize each target position. The first clutch 8 is adjusted so that the voltages V1_sft3 and V2_sft3 applied to the motor 75b are adjusted, the engine torque command value TTe is set, and the first clutch 8 and the second clutch 9 have desired transmission torques Tcl and Tclb. The first clutch motor 7 is set so that the target position of the second clutch 9 is set and each target position is realized. Voltage V1_cl1 applied to b, V2_cl1, voltage V1_cl2 applied to the second clutch motor 72b, to adjust the V2_cl2.

  Further, the transmission control unit 100 predicts the next shift speed based on the current target shift speed, the vehicle speed Vsp calculated from the output shaft rotational speed No, the accelerator pedal depression amount Aps, and the like. Based on the prediction result, the first shift motor is configured to release / engage a desired synchronous meshing mechanism in order to bring a predetermined synchronous meshing mechanism used for achieving the predicted shift speed into a meshing state. The voltages V1_sft1 and V2_sft1 applied to 73b, the voltages V1_sft2 and V2_sft2 applied to the second shift motor 74b, and the voltages V1_sft3 and V2_sft3 applied to the third shift motor 75b are adjusted. For example, when traveling at 2nd speed, that is, when the target shift speed is 2nd speed, it is predicted based on the driving state whether the next shift speed will be 1st speed or 3rd speed. Then, the voltages V1_sft1 and V2_sft1 applied to the first shift motor 73b are adjusted in advance so that the first synchronous engagement mechanism 21 is engaged with the first driven gear 11 or the third driven gear 13.

  Further, the transmission control unit 100 sets the target shift speed from the vehicle speed Vsp calculated from the output shaft rotation speed No and the accelerator pedal depression amount Aps, and executes the shift operation to the set shift speed. The command value TTe is set, and the target positions of the first clutch 8 and the second clutch 9 are set so that the first clutch 8 and the second clutch 9 have desired transmission torques Tcl and Tclb, and each target position is realized. Thus, the voltages V1_cl1 and V2_cl1 applied to the first clutch motor 71b and the voltages V1_cl2 and V2_cl2 applied to the second clutch motor 72b are adjusted. Further, when the predicted result of the shift speed is different from the target shift speed, the voltages V1_sft1, V2_sft1, and the second applied to the first shift motor 73b so as to release / engage the desired synchronous meshing mechanism. The voltages V1_sft2 and V2_sft2 applied to the 2-shift motor 74b and the voltages V1_sft3 and V2_sft3 applied to the third shift motor 75b are adjusted.

  For example, when driving at 3rd speed, that is, when the target shift speed is at 3rd speed, it is predicted based on the driving state whether the next shift speed will be at 2nd speed or 4th speed. When the next gear position is predicted to be the second speed and the target gear position is switched from the third speed to the second speed from the state in which the third synchronous mesh mechanism 23 is engaged with the second driven gear 12 in advance. That is, when the downshift command is issued, since the third synchronous meshing mechanism 23 is already in mesh with the second driven gear 12, the engagement of the first clutch 8 can be started. If the target gear stage is switched from the 3rd speed to the 2nd speed from the state in which the 3rd synchronous meshing mechanism 23 is meshed with the 4th driven gear 14 in advance when the 4th speed is predicted, Before starting the fastening, the third synchronous meshing mechanism 23 is Releasing the meshing state between Ngia 14, it is necessary to make meshes with the second driven gear 12. Thus, the accuracy of the prediction result of the next gear stage greatly affects the responsiveness from when the target gear stage is set until the gear shift is completed.

Next, specific control contents of the preshift control of the control device for the automatic transmission for a vehicle according to the present embodiment will be described with reference to FIGS.
First, the entire control contents of the shift control including the preshift control of the control device for the vehicle automatic transmission according to the present embodiment will be described with reference to FIG.
FIG. 3 is a flowchart showing the entire control contents of the shift control including the pre-shift control of the control device for the automatic transmission for a vehicle according to the embodiment of the present invention.

  The control flow includes step 301 (target gear position calculation), step 302 (standby gear position calculation), and step 303 (shift control).

  The control contents in FIG. 3 are programmed in the computer 100c of the transmission control unit 100 and are repeatedly executed at a predetermined cycle. That is, the following processes of steps 301 to 303 are repeatedly executed by the transmission control unit 100 at a predetermined cycle.

  In step 301 (target gear position calculation), the transmission control unit 100 determines the shift lever position (P range, R range, N range, D range, M range that allows the driver to perform a shift operation). RngPos, the up switch signal UpSw (upshift command signal) by the driver's operation, the down switch signal DnSw (downshift command signal), the vehicle speed Vsp calculated from the output shaft rotational speed No, the accelerator pedal depression amount Aps, etc. A target gear position tGP_nxt is set based on the operating state. For example, when the range position signal RngPos is in the D range (in the automatic transmission mode), the target gear position tGP_nxt is set from the vehicle speed Vsp calculated from the output shaft rotation speed No, the accelerator pedal depression amount Aps, and the like. When the range position signal RngPos is in the M range (in the manual shift mode), the target gear position tGP_nxt is set from the up switch signal UpSw and the down switch signal DnSw.

  In step 302 (standby gear position calculation), the transmission control unit 100 predicts the next shift speed and sets the target standby position tGP_stb. Details of step 302 (standby gear position calculation) will be described later with reference to FIG.

  In step 303 (shift control), the transmission control unit 100 sets the target gear position tGP_nxt set in step 301 (target gear position calculation) and the target standby position tGP_stb set in step 302 (standby gear position calculation). Is set to the target position of the first synchronization meshing mechanism 21, the second synchronization meshing mechanism 22, and the third synchronization meshing mechanism 23, and the voltage applied to the first shift motor 73b so as to realize each target position. V1_sft1, V2_sft1, voltages V1_sft2, V2_sft2 applied to the second shift motor 74b, and voltages V1_sft3, V2_sft3 applied to the third shift motor 75b are adjusted. As a result, the sleeve 1 position RPslv1, the sleeve 2 position RPslv2, and the sleeve 3 position RPslv3, which indicate the stroke positions of the first synchronization engagement mechanism 21, the second synchronization engagement mechanism 22, and the third synchronization engagement mechanism 23, respectively. Follow the target position.

Next, details of step 302 (standby gear position calculation) in FIG. 3 will be described with reference to FIG.
FIG. 4 is a flowchart showing the contents of the standby gear position calculation process in the preshift control of the control device for the automatic transmission for a vehicle according to the embodiment of the present invention.

  In step 401, the transmission control unit 100 operates such as the target gear position tGP_nxt, the range position signal RngPos, the vehicle speed Vsp, and the accelerator pedal depression amount Aps set in step 301 (target gear position calculation) in FIG. Is set to the standby gear position candidate value tGP_stb0.

  In step 402, the transmission control unit 100 determines whether a shift is being performed or whether the range position signal RngPos is in the P range, the R range, or the N range. If shifting is in progress, or if the range position signal RngPos is in the P range, R range, or N range, the process proceeds to step 409, and the standby candidate value tGP_stb0 is substituted for the target standby position tGP_stb, and the right turn intention display signal Rturn is input. The elapsed time measurement timer Tr and the elapsed time measurement timer Tl from the left turn intention display signal Lturn input are cleared. If the speed is not being changed and the range position signal RngPos is not any of the P range, R range, and N range, the process proceeds to step 403.

  In step 403, the transmission control unit 100 determines whether or not it is in the high speed range. It is determined whether or not a value obtained by multiplying the output shaft rotational speed No by a gear ratio Gnxt corresponding to the target gear position tGP_nxt set in step 301 (target gear position calculation) in FIG. . If it is greater than or equal to Nh, it is a high speed range, so the routine proceeds to step 409, where the standby candidate value tGP_stb0 is substituted for the target standby position tGP_stb, the elapsed time measurement timer Tr from the right turn intention display signal Rturn input, and the left turn intention display The measurement timer Tl of the elapsed time from the signal Lturn input is cleared. If it is less than the threshold value Nh, the process proceeds to step 404. Here, the threshold value Nh is desirably set based on the allowable maximum rotational speed of the engine 7 that is a driving force source and the allowable maximum rotational speed of the transmission 50. Set a value that does not exist. The threshold value Nh is desirably set individually for each gear position. Further, the determination in step 403 may be configured to provide hysteresis so that YES is obtained when the threshold value is equal to or greater than the threshold value Nh, NO is determined when the threshold value is equal to or less than the threshold value Nl, and otherwise the previous determination is followed.

  In step 404, the transmission control unit 100 determines whether the mode is the auto mode or the manual mode. It is determined whether the range position signal RngPos is the D range (automatic transmission mode) or the M range (manual transmission mode). In the case of the automatic transmission mode, the process proceeds to step 405, and in the case of the manual transmission mode, the process proceeds to step 407.

  In step 405, the transmission control unit 100 calculates the elapsed time Tr from the input of the right turn intention display signal Rturn and determines whether or not the elapsed time Tr is within a predetermined range. Since the right turn intention display signal of the direction indicator is an ON / OFF flashing signal, the elapsed time Tr calculation in step 405 is performed when the right turn intention display signal Rturn is turned from OFF to ON in the state of Tr = 0. Elapsed time measurement is started, and when Tr ≧ Tr_max, Tr = 0 is performed. For example, when the right turn intention display signal Rturn blinks three times, measurement of the elapsed time from the first OFF → ON time is started, and Tr = 0 is set when Tr ≧ Tr_max. When TrA1 ≦ Tr ≦ TrA2, the routine proceeds to step 410, where the target standby position tGP_stb is set to the target gear position tGP_nxt−1, that is, the target gear position tGP_nxt is one step downshift side. If TrA1 ≦ Tr ≦ TrA2, the process proceeds to step 406.

  In step 406, the transmission control unit 100 calculates the elapsed time Tl from the input of the left turn intention display signal Lturn and determines whether or not the elapsed time Tl is within a predetermined range. Similar to the right turn intention display signal Rturn, the elapsed time Tl calculation in step 406 starts the measurement of the elapsed time from the time when the left turn intention display signal Lturn changes from OFF to ON in the state of Tl = 0, and Tl ≧ Tl_max. A process of setting Tl = 0 at the time is performed. When TlA1 ≦ Tl ≦ TlA2, the routine proceeds to step 410, where the target standby position tGP_stb is set to the target gear position tGP_nxt−1, that is, the target gear position tGP_nxt is one step downshift side. If TlA1 ≦ Tl ≦ TlA2, the process proceeds to step 411, and the standby candidate value tGP_stb0 is substituted into the target standby position tGP_stb.

  In step 407, as in step 405, the transmission control unit 100 calculates the elapsed time Tr from the input of the right turn intention display signal Rturn and determines whether or not the elapsed time Tr is within a predetermined range. When TrM1 ≦ Tr ≦ TrM2, the routine proceeds to step 412, where the target standby position tGP_stb is set to the target gear position tGP_nxt−1, that is, the target gear position tGP_nxt is one step downshift side. If TrM1 ≦ Tr ≦ TrM2, the process proceeds to step 408.

  In step 408, as in step 406, the transmission control unit 100 calculates the elapsed time Tl from the input of the left turn intention display signal Lturn and determines whether or not the elapsed time Tl is within a predetermined range. When TlM1 ≦ Tl ≦ TlM2, the routine proceeds to step 412 where the target standby position tGP_stb is set to the target gear position tGP_nxt−1, that is, the target gear position tGP_nxt is one step downshift side. If TlM1 ≦ Tl ≦ TlM2, the process proceeds to step 413, and the standby candidate value tGP_stb0 is substituted into the target standby position tGP_stb.

  With this configuration, the target standby position tGP_stb is placed on standby on the downshift side after a predetermined time has elapsed after the driver's operation using the direction indicator. That is, a predetermined delay time is provided until the downshift side standby is set. This delay time is to prevent the preshift control from being erroneously controlled based on an erroneous operation of the direction indicator. Further, when no shift is performed until a predetermined time has elapsed, the standby candidate value tGP_stb0 is obtained.

  It should be noted that there are many cases where the shift responsiveness request is different depending on whether it is the auto mode or the manual mode, that is, whether the range position signal RngPos is the D range (automatic shift mode) or the M range (manual shift mode). Therefore, it is desirable that the elapsed time determination values TrA1 and TlA1 and TrM1 and TlM1 are set as different setting values, and it is further desirable that TrA1 <TrM1 and TlA1 <TlM1.

  Further, for example, the vehicle operation after the operation by the direction indicator is different depending on the traveling vehicle speed, such as overtaking acceleration at a high speed and turning right or left at an intersection at a low speed. , TrA2, TlA1, TlA2, TrM1, TrM2, TlM1, and TlM2 are preferably configured as a function of vehicle speed. For example, when an intention to turn right is displayed at high speed, it is generally assumed that the vehicle is overtaking due to a lane change. When a right turn intention is displayed at a low speed, a right turn at an intersection or the like is generally assumed. Here, the time until the lane is changed after the right turn intention is displayed is shorter than when the right turn is displayed after the right turn intention is displayed. Therefore, the determination value TrA1 (H) at the time of high speed is set smaller than the determination value TrA1 (L) at the time of low speed (TrA1 (H) <TrA1 (L)). Furthermore, it is good also as a structure divided and set for every present gear position.

  In addition, although the left-hand traffic in Japan is different from the right-hand traffic in the United States, the direction of vehicle traffic differs depending on the country. For example, in the case of Japan, TrA1 <TlA1, TrM1 < When TlM1 is set and the vehicle speed is low, a left turn is assumed and TrA1> TlA1 and TrM1> TlM1. In the case of right-hand traffic such as the United States, TrA1> TlA1, TrM1> TlM1 assuming overtaking acceleration when the vehicle speed is high, and TrA1 <TlA1, TrM1 <T1M1 assuming left turn when the vehicle speed is low. To do. Thus, it is desirable to set according to the vehicle speed and right and left.

  In addition to the configuration shown in FIG. 4, even in the case of a so-called hazard signal in which the right turn intention display signal Rturn and the left turn intention display signal Lturn blink simultaneously, the target standby position tGP_stb after a predetermined time has elapsed after the operation by the driver. May be configured to be the standby candidate value tGP_stb0 when the shift is on the downshift side and the shift is not performed until a predetermined time has elapsed. Here, the hazard signal may be identified by using both the right turn intention display signal Rturn and the left turn intention display signal Lturn ON / OFF signal, or the hazard signal buttons and switches may be input to the transmission. It may be configured to input to the control unit 100, or can be configured using another mechanism for the transmission control unit 100 to identify the operation of the hazard signal. When a hazard signal switch is input, a determination may be made based on the ON duration of the switch. When using both ON / OFF signals for identification, in addition to measuring the elapsed time from the time when the state is changed from OFF to ON as in the configuration shown in step 405, the determination is made by repeating the ON signal a predetermined number of times. The method is preferred. For example, the measurement of the elapsed time from the time when both the right turn intention display signal Rturn and the left turn intention display signal Lturn are first turned from OFF to ON is started, and when the third turn is turned ON, the target is set as in step 410. The standby position tGP_stb is set to the target gear position tGP_nxt−1, that is, the target gear position tGP_nxt is set one shift down, etc.

Next, the first control example of the preshift control of the control device for the vehicle automatic transmission according to the present embodiment will be described with reference to FIG.
FIG. 5 is a timing chart showing the control contents of the first control example of the preshift control of the control device for the vehicle automatic transmission according to the embodiment of the present invention.

  In the first control example shown in FIG. 5, the right turn intention display signal Rturn is input in a state where the vehicle is traveling at the third speed of the M range (manual shift mode), and thereafter, from the third speed to the second speed. This is a case where the downshift is executed.

  5, FIG. 5A shows the target gear position tGP_nxt, FIG. 5B shows the standby candidate value tGP_stb0, and FIG. 5C shows the right turn intention display signal Rturn. 5D shows the left turn intention display signal Lturn, FIG. 5E shows the target standby position tGP_stb, and FIG. 5F shows the sleeve 3 position RPslv3 that is the position of the third synchronous meshing mechanism 23.

  Prior to time t1, the vehicle is in a steady running state, the target gear position tGP_nxt in FIG. 5A is the third speed, the standby candidate value tGP_stb0 in FIG. 5B and the target standby position tGP_stb in FIG. As shown in FIG. 5 (F), the sleeve 3 position RPslv3 is meshed with the fourth speed side.

  At time t1, the driver operates the direction indicator 107, and as shown in FIG. 5C, the right turn intention display signal Rturn turns from OFF to ON. The elapsed time Tr from the input of the right turn intention display signal Rturn is calculated at step 407 in FIG. 4, and at time t2 when TrM1 ≦ Tr, the target standby position tGP_stb = target gear position tGP_nxt− at step 407 and step 412 in FIG. 1, that is, the first gear downshift side relative to the target gear position tGP_nxt is changed from the fourth speed to the second speed as shown in FIG. The voltages V1_sft3 and V2_sft3 applied to the third shift motor 75b are adjusted by step 303 in FIG. 3, and the sleeve 3 position RPslv3 moves from the 4th speed side to the 2nd speed side as shown in FIG. At t3, the sleeve 3 position RPslv3 is engaged with the second speed side.

  At time t4, the down switch of the lever device 106 is operated by the driver. At step 301 (target gear position calculation) in FIG. 3, as shown in FIG. Switch to speed.

  At time t4, the sleeve 3 position RPslv3 is engaged with the second speed side. Therefore, the speed change operation after time t4 is performed while the second clutch 9 that has formed the third speed is disengaged. Thus, the first clutch 8 is engaged to form the shift, and the response from the time t4 when the shift operation is started until the shift is completed can be improved.

Next, a second control example of the preshift control of the control device for the vehicle automatic transmission according to the present embodiment will be described with reference to FIG.
FIG. 6 is a timing chart showing the control content of the second control example of the preshift control of the control device for the vehicle automatic transmission according to the embodiment of the present invention. 6A to 6F are the same as FIGS. 5A to 5F.

  In the second control example shown in FIG. 6, the left turn intention display signal Lturn is input while the vehicle is traveling in the third speed of the M range (manual shift mode), and then the third speed is changed to the second speed. This is a case where the downshift is executed.

  Before time t1, the vehicle is in a steady running state, the target gear position tGP_nxt in FIG. 6 (A) is the third speed, the standby candidate value tGP_stb0 in FIG. 6 (B), and the target standby position tGP_stb in FIG. As shown in FIG. 6 (F), the sleeve 3 position RPslv3 is in mesh with the fourth speed side.

  At time t1, the driver operates the direction indicator 107, and as shown in FIG. 6D, the left turn intention display signal Lturn is turned from OFF to ON. The elapsed time Tl from the left turn intention display signal Lturn input is calculated at step 408 in FIG. 4, and at time t2 when TlM1 ≦ Tl, the target standby position tGP_stb = target gear position tGP_nxt− at step 408 and step 412 in FIG. 1, that is, the first gear downshift side with respect to the target gear position tGP_nxt, and changes from the fourth speed to the second speed as shown in FIG. The voltages V1_sft3 and V2_sft3 applied to the third shift motor 75b are adjusted by step 303 in FIG. 3, and the sleeve 3 position RPslv3 is moved from the 4th speed side to the 2nd speed side as shown in FIG. At t3, the sleeve 3 position RPslv3 is engaged with the second speed side.

  At time t4, the driver operates the down switch of the lever device 106, and in step 301 (target gear position calculation) in FIG. 3, as shown in FIG. Switch to.

  At time t4, the sleeve 3 position RPslv3 is engaged with the second speed side. Therefore, the speed change operation after time t4 is performed while the second clutch 9 that has formed the third speed is disengaged. Thus, the first clutch 8 is engaged to form the shift, and the response from the time t4 when the shift operation is started until the shift is completed can be improved.

Next, a third control example of the preshift control of the control device for the vehicle automatic transmission according to the present embodiment will be described with reference to FIG.
FIG. 7 is a timing chart showing the control content of the third control example of the preshift control of the control device for the vehicle automatic transmission according to the embodiment of the present invention. 7A to 7F are the same as FIGS. 5A to 5F.

  In the third control example shown in FIG. 7, the right turn intention display signal Rturn is input in a state where the vehicle is traveling in the fifth speed of the D range (automatic shift mode), and then, from the fifth speed to the fourth speed. This is a case where the downshift is executed.

  Before time t1, the vehicle is in a steady running state, the target gear position tGP_nxt in FIG. 7A is the fifth speed, the standby candidate value tGP_stb0 in FIG. 7B and the target standby position tGP_stb in FIG. As shown in FIG. 7F, the sleeve 3 position RPslv3 is in the neutral position.

  At time t1, the driver operates the direction indicator 107, and as shown in FIG. 7C, the right turn intention display signal Rturn turns from OFF to ON. In step 405 of FIG. 4, the elapsed time Tr from the input of the right turn intention display signal Rturn is calculated, and at time t2 when TrA1 ≦ Tr, the target standby position tGP_stb = target gear position tGP_nxt− at step 405 and step 410 of FIG. 1, i.e., the target gear position tGP_nxt is set to the one-stage downshift side, and the speed is changed from N (neutral) to 4th as shown in FIG. The voltages V1_sft3 and V2_sft3 to be applied to the third shift motor 75b are adjusted by step 303 in FIG. 3, and the sleeve 3 position RPslv3 is moved from the neutral position to the fourth speed side as shown in FIG. Thus, the sleeve 3 position RPslv3 is engaged with the fourth speed side.

  At time t4, the accelerator pedal is depressed by the driver for, for example, overtaking acceleration, and the accelerator pedal depression amount Aps is increased, so that in step 301 (target gear position calculation) of FIG. As shown in A), the target shift speed is switched from the fifth speed to the fourth speed.

  At time t4, the sleeve 3 position RPslv3 is engaged with the fourth speed side, so that the speed change operation after time t4 is performed while the second clutch 9 that has formed the fifth speed is disengaged. Thus, the first clutch 8 is engaged to form the shift, and the response from the time t4 when the shift operation is started until the shift is completed can be improved.

Next, a fourth control example of the preshift control of the control device for the vehicle automatic transmission according to the present embodiment will be described with reference to FIG.
FIG. 8 is a timing chart showing the control content of the fourth control example of the preshift control of the control device for the vehicle automatic transmission according to the embodiment of the present invention. 8A to 8F are the same as FIGS. 5A to 5F.

  In the fourth control example shown in FIG. 8, the right turn intention display signal Rturn is input in the state where the vehicle is traveling at the fifth speed of the D range (automatic shift mode), but the shift operation is not started thereafter. Is the case.

  Prior to time t1, the vehicle is in a steady running state, the target gear position tGP_nxt in FIG. 8A is the fifth speed, the standby candidate value tGP_stb0 in FIG. 8B and the target standby position tGP_stb in FIG. As shown in FIG. 8F, the sleeve 3 position RPslv3 is in the neutral position.

  At time t1, the driver operates the direction indicator 107, and as shown in FIG. 8C, the right turn intention display signal Rturn turns from OFF to ON. In step 405 of FIG. 4, the elapsed time Tr from the input of the right turn intention display signal Rturn is calculated, and at time t2 when TrA1 ≦ Tr, the target standby position tGP_stb = target gear position tGP_nxt− at step 405 and step 410 of FIG. 1, i.e., one gear downshift side relative to the target gear position tGP_nxt, and, as shown in FIG. The voltages V1_sft3 and V2_sft3 to be applied to the third shift motor 75b are adjusted by step 303 in FIG. 3, and the sleeve 3 position RPslv3 is moved from the neutral position to the fourth speed side as shown in FIG. Thus, the sleeve 3 position RPslv3 is engaged with the fourth speed side.

  After time t3, the speed change operation is not started, and at time t4 when the elapsed time Tr from the right turn intention display signal Rturn input becomes larger than TrA2 in step 405 in FIG. 4, the target standby position tGP_stb in step 411 in FIG. = Standby candidate value tGP_stb0 is set, and, as shown in FIG. 8 (E), the fourth speed is changed to N (neutral). The voltages V1_sft3 and V2_sft3 applied to the third shift motor 75b are adjusted by step 303 in FIG. 3, and the sleeve 3 position RPslv3 is moved from the fourth speed side to the neutral position as shown in FIG. Thus, the sleeve 3 position RPslv3 becomes the neutral position.

Next, a fifth control example of the preshift control of the control device for the vehicle automatic transmission according to the present embodiment will be described with reference to FIG.
FIG. 9 is a timing chart showing the control content of the fifth control example of the preshift control of the control device for the vehicle automatic transmission according to the embodiment of the present invention. 9A to 9F are the same as FIGS. 5A to 5F.

  In the fifth control example shown in FIG. 9, even in the case of a so-called hazard signal in which the right turn intention display signal Rturn and the left turn intention display signal Lturn blink simultaneously, the target standby position tGP_stb after a predetermined time has elapsed after the operation by the driver. This is a control example of pre-shift control when configured so as to be on the downshift side standby. This example is a case where a hazard signal is input in a state where the vehicle is traveling at the fifth speed in the M range (manual shift mode), and then a downshift from the fifth speed to the fourth speed is executed. .

  Prior to time t1, the vehicle is in a steady running state, the target gear position tGP_nxt in FIG. 9A is the fifth speed, the standby candidate value tGP_stb0 in FIG. 9B and the target standby position tGP_stb in FIG. As shown in FIG. 9F, the sleeve 3 position RPslv3 is in the neutral position.

  At time t1, the hazard signal is operated by the driver, and both the right turn intention display signal Rturn in FIG. 9C and the left turn intention display signal Lturn in FIG. 9D are turned from OFF to ON. The elapsed time from the input of both the right turn intention display signal Rturn and the left turn intention display signal Lturn is calculated, the elapsed time exceeds the set threshold, and the right turn intention display signal Rturn and the left turn intention display signal Lturn are both the third time. At time t2 when turning from OFF to ON, the target standby position tGP_stb = target gear position tGP_nxt−1, that is, set to the one-stage downshift side relative to the target gear position tGP_nxt, and as shown in FIG. ) To 4th speed. Voltages V1_sft3 and V2_sft3 to be applied to the third shift motor 75b are adjusted by step 303 in FIG. 3, and as shown in FIG. 9F, the sleeve 3 position RPslv3 moves from the neutral position to the fourth speed side, and time t3 Thus, the sleeve 3 position RPslv3 is engaged with the fourth speed side.

  At time t4, the driver operates the down switch of the lever device 106, and in step 301 (target gear position calculation) in FIG. 3, as shown in FIG. Switch to.

  At time t4, the sleeve 3 position RPslv3 is engaged with the fourth speed side, so that the speed change operation after time t4 is performed while the second clutch 9 that has formed the fifth speed is disengaged. Thus, the first clutch 8 is engaged to form the shift, and the response from the time t4 when the shift operation is started until the shift is completed can be improved.

  Next, a second configuration example of the vehicle automatic transmission and the control device according to the present embodiment will be described with reference to FIG.

  FIG. 10 is a skeleton diagram of a system configuration example showing a configuration of an automatic transmission for a vehicle and a control device according to an embodiment of the present invention. The same reference numerals as those in FIG. 1 indicate the same parts.

  In this configuration example, the difference from the configuration example shown in FIG. 1 is that the first clutch 8 and the first clutch 9 that transmit the torque of the engine 7 in the example of FIG. On the other hand, in this example, a wet multi-plate clutch is used.

  The automatic transmission 51 is provided with a first clutch 1008 and a second clutch 1009 that are friction transmission mechanisms. By engaging and releasing the first clutch 98, the torque of the engine 7 is supplied to the first input shaft 41. It is possible to transmit to and shut off. In addition, the torque of the engine 7 can be transmitted to and cut off from the second input shaft 42 by engaging and releasing the second clutch 99.

  The transmission control unit 100 controls the pressure plate (not shown) provided in the first clutch 1008 by controlling the current of the electromagnetic valve 105 a provided in the hydraulic mechanism 105, and the transmission of the first clutch 1008. Torque is controlled.

  Further, the transmission control unit 100 controls the pressure plate (not shown) provided in the second clutch 1009 by controlling the current of the electromagnetic valve 105 b provided in the hydraulic mechanism 105, and the second clutch 1009. The transmission torque is controlled.

  Further, the transmission control unit 100 controls the currents of the electromagnetic valve 105c and the electromagnetic valve 105d provided in the hydraulic mechanism 105, whereby a hydraulic piston (not shown) and a shift fork (not shown) provided in the shift actuator 61 are controlled. The position or load of the first synchronous meshing mechanism 21 is controlled through engagement with the first driven gear 11 or the third driven gear 13, so that the rotational torque of the second input shaft 42 can be increased. It can be transmitted to the output shaft 43 via the 1-synchronizing mechanism 21. Here, by increasing the current of the solenoid valve 105d, a load is applied in the direction in which the first synchronous meshing mechanism 21 moves to the first driven gear 11 side, and by increasing the current of the solenoid valve 105c, the first A load is applied in a direction in which the synchronous meshing mechanism 21 moves to the third driven gear 13 side. The shift actuator 61 is provided with a position sensor (not shown) that measures the position of the first synchronous meshing mechanism 21.

  Further, the transmission control unit 100 controls the currents of the solenoid valve 105e and the solenoid valve 105f provided in the hydraulic mechanism 105, whereby the hydraulic piston (not shown) and the shift fork (not shown) provided in the shift actuator 62 are controlled. The position or load of the second synchronous meshing mechanism 22 is controlled via the second driven gear 15 to engage the fifth driven gear 15 with the rotational torque of the second input shaft 42. To the output shaft 43. The shift actuator 62 is provided with a position sensor 62a (not shown) that measures the position of the second synchronous meshing mechanism 22.

  Further, the transmission control unit 100 controls the currents of the solenoid valve 105g and the solenoid valve 105h provided in the hydraulic mechanism 105, whereby a hydraulic piston (not shown) and a shift fork (not shown) provided in the shift actuator 63 are controlled. The position or load of the third synchronous meshing mechanism 23 is controlled via the second driven gear 12 or the fourth driven gear 14, so that the rotational torque of the first input shaft 41 can be increased. It can be transmitted to the output shaft 43 via the three-synchronization meshing mechanism 23. Note that the shift actuator 63 is provided with a position sensor (not shown) for measuring the position of the third synchronous meshing mechanism 23.

  Thus, from the first drive gear 1, the second drive gear 2, the third drive gear 3, the fourth drive gear 4, and the fifth drive gear 5, the first driven gear 11, the second driven gear 12, and the third driven gear. 13, the rotational torque of the transmission input shaft 41 transmitted to the transmission output shaft 43 via the fourth driven gear 14 and the fifth driven gear 15 is a differential gear (not shown) connected to the transmission output shaft 43. To the axle (not shown).

  In this way, the first clutch, the second clutch, the first synchronization meshing mechanism 21, the second synchronization meshing mechanism 22, and the other mechanism for controlling the third synchronization meshing mechanism 23 can be used. is there.

As described above, according to the present embodiment, in addition to the preshift control based on the prediction result of the next shift stage, when the direction indicator is operated, the desired gear is set in advance before the start of the subsequent shift. It is possible to stand by, shorten the time from the start of the shift operation to the completion of the shift, and improve the response of the shift.

1 is a skeleton diagram of a system configuration example illustrating a configuration of an automatic transmission for a vehicle and a control device according to an embodiment of the present invention. It is a block diagram which shows the input / output signal relationship between the transmission control unit and engine control unit in the control apparatus of the automatic transmission for vehicles which concerns on one Embodiment of this invention. It is a flowchart which shows the control content of the whole shift control including the pre shift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. It is a flowchart which shows the content of the standby gear position calculation process in the preshift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. It is a timing chart which shows the control content of the 1st control example of the preshift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. It is a timing chart which shows the control content of the 2nd control example of the preshift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. It is a timing chart which shows the control content of the 3rd control example of the pre shift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. It is a timing chart which shows the control content of the 4th control example of the pre shift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. It is a timing chart which shows the control content of the 5th control example of the preshift control of the control apparatus of the automatic transmission for vehicles by one Embodiment of this invention. 1 is a skeleton diagram of a system configuration example illustrating a configuration of an automatic transmission for a vehicle and a control device according to an embodiment of the present invention.

DESCRIPTION OF SYMBOLS 1 ... 1st drive gear 2 ... 2nd drive gear 3 ... 3rd drive gear 4 ... 4th drive gear 5 ... 5th drive gear 7 ... Engine 8 ... 1st clutch 9 ... 2nd clutch 11 ... 1st driven gear 12 2nd driven gear 13 ... 3rd driven gear 14 ... 4th driven gear 15 ... 5th driven gear 21 ... 1st synchronous meshing mechanism 22 ... 2nd synchronous meshing mechanism 23 ... 3rd synchronous meshing mechanism 31 ... 1st 1 input shaft rotation sensor 32 ... 2nd input shaft rotation sensor 33 ... output shaft rotation sensor 41 ... transmission 1st input shaft 42 ... transmission 2nd input shaft 43 ... output shaft 50 ... automatic transmission 71 ... 1st clutch actuator 72 ... 2nd clutch actuator 73 ... 1st shift actuator 74 ... 2nd shift actuator 75 ... 3rd shift actuator 100 ... Transmission control unit 101 ... Engine The control unit 103 ... Communication unit 106 ... lever device 107 ... direction indicator 201 ... accelerator opening sensor 202 ... brake switch

Claims (5)

A plurality of friction transmission mechanisms for transmitting and interrupting the power of the driving force source; a plurality of transmission input shafts respectively coupled to the plurality of friction transmission mechanisms; and the plurality of transmission input shafts and the transmission output shafts. Used for control of an automatic transmission having a plurality of gear trains selectively connected by a selection operation of a plurality of synchronous mesh mechanisms,
The transmission input shaft to which one of the friction transmission mechanisms is connected and the transmission output shaft are connected via a gear train, and one friction transmission mechanism is engaged and the other friction transmission mechanism is connected. To achieve the desired gear stage,
When the predetermined gear stage is achieved, the next gear stage is predicted using at least one parameter of the rotation speed of the transmission output shaft, the vehicle speed, or the depression amount of the accelerator pedal, and this prediction Based on the result, the transmission input shaft and the transmission output shaft to which the friction transmission mechanism that is not used for achieving the current gear stage is connected by operating the predetermined synchronous meshing mechanism. Is a shift control device for an automatic transmission for a vehicle that performs pre-shift control in which the motor is connected and waited via a predetermined gear train,
Control that performs pre-shift control that operates the predetermined synchronous meshing mechanism to make the driver wait on the downshift side from the current shift stage when the direction indicator indicating the driver's intention to turn right or turn left is operated. A shift control apparatus for an automatic transmission for a vehicle, characterized in that it comprises means. The shift control device for an automatic transmission for a vehicle according to claim 1,
The control means includes
When the direction indicator is operated, the predetermined synchronous meshing mechanism is operated, and pre-shift control is performed to wait on the downshift side from the current shift stage,
If the speed change operation is not started in a period from when the direction indicator is operated until a predetermined time elapses, at least of the rotation speed of the transmission output shaft, the vehicle speed, or the depression amount of the accelerator pedal The transmission input shaft and the transmission to which the friction transmission mechanism that is not used to achieve the current shift speed is connected based on the prediction result of the next shift speed using one parameter A shift control apparatus for an automatic transmission for a vehicle, wherein preshift control is performed in which the output shaft is connected to a standby state via a predetermined gear train and is placed on standby. The shift control device for an automatic transmission for a vehicle according to claim 1,
The control means performs pre-shift control in which a predetermined delay time has elapsed since the operation of the direction indicator is operated, and the predetermined synchronization mechanism is operated to wait on the downshift side from the current shift stage. A shift control device for an automatic transmission for a vehicle, wherein: The shift control apparatus for an automatic transmission for a vehicle according to claim 3,
The shift control device for an automatic transmission for a vehicle, wherein the control means varies the delay time depending on whether the direction indicator is operated to make a right turn or to make a left turn. The shift control apparatus for an automatic transmission for a vehicle according to claim 3,
The shift control device for an automatic transmission for a vehicle, wherein the control means changes the delay time according to a vehicle speed.

Images