JP6834216B2 - Transmission control device - Google Patents

Description

The present invention relates to a transmission control device including a transmission mechanism, a torque converter, and a transmission clutch.

Conventionally, a transmission having a torque converter between the engine and the transmission mechanism is known. Some torque converters have a lockup clutch that can mechanically connect the input side and the output side.

In recent years, in a transmission equipped with a torque converter having a lockup clutch, a transmission equipped with a transmission clutch for controlling disconnection and disconnection of a driving force at the time of shifting has appeared between the torque converter and the transmission mechanism. There is.

As a technology for transmissions equipped with a torque converter and a clutch, when the vehicle speed is low and the gear is not shifting, the lockup clutch is locked up and the clutch is slipped to improve drivability and fuel efficiency. (For example, see Patent Document 1).

Japanese Unexamined Patent Publication No. 2004-257518

For example, when the vehicle speed increases, it is necessary to engage the lockup clutch of the torque converter to establish a transmission path of the driving force from the engine to the drive wheels via the lockup clutch. The fastening force of the lockup clutch of the torque converter is, for example, the difference in the pressure of the hydraulic oil supplied to each of the two hydraulic chambers in the torque converter provided via the piston for driving the lockup clutch, that is, 2. It is controlled by the differential pressure of one hydraulic chamber. Therefore, the lockup clutch has relatively poor responsiveness and controllability. Therefore, when the lockup clutch is engaged by controlling only the lockup clutch of the torque converter, a shock may occur when the lockup clutch is engaged.

Further, it is required to quickly establish a transmission path of driving force through a lockup clutch from the engine to the driving wheels.

Therefore, the present invention can reduce the occurrence of shock when establishing a drive force transmission path from a drive source to a drive wheel via a lockup clutch, and can quickly set the drive force transmission path. The purpose is to provide a technology that can be established.

In order to achieve the above object, the transmission control device according to one aspect of the present invention is provided between the transmission mechanism, the drive source and the transmission mechanism, an impeller connected to the drive source side, and the transmission mechanism. It has a clutch connected to the side, and power can be transmitted between the impeller and the clutch via hydraulic oil, and power can be transmitted by mechanically connecting the drive source side and the clutch. A transmission having a torque converter having a lockup clutch capable of controlling the clutch, and a transmission clutch arranged between the torque converter and the transmission mechanism and capable of controlling the transmission of power between the torque converter and the transmission mechanism. The lockup clutch is a control device of the lockup clutch, and the fastening force can be adjusted by the hydraulic pressure of the hydraulic oil supplied to the hydraulic chamber on one side of the piston that presses the clutch disc of the lockup clutch. When the start determination means for determining whether or not the predetermined condition for engaging the lockup clutch is satisfied and the start determination means determines that the predetermined condition is satisfied, the shift clutch is put into a slip state and can be transmitted by the shift clutch. The first clutch control means that controls the allowable torque to match the torque of the turbine, and the hydraulic oil to the hydraulic chamber to engage the lockup clutch when the allowable torque matches the torque of the turbine. After the lockup clutch control means for starting the control of the hydraulic pressure and the control of the hydraulic pressure by the lockup clutch control means are started, the speed is changed until at least there is a difference between the rotation speed of the turbine and the rotation speed of the input shaft of the transmission mechanism. A second clutch control means for controlling the slip state of the speed change clutch is provided so that the allowable torque of the clutch matches the torque of the turbine at the start of hydraulic control.

In the control device of the transmission, the lockup clutch control means hydraulically operates by turning on the on / off valve between the hydraulic chamber and the hydraulic oil supply source when the allowable torque matches the torque of the turbine. Control of the hydraulic supply of hydraulic fluid to the chamber may be initiated.

Further, in the control device of the transmission, the torque of the turbine at the start of the control of the hydraulic pressure may be less than or equal to the torque required by the driver, which is assumed to be required by the driver for the drive source.

Further, in the control device of the transmission, the second clutch control means hydraulically reduces the allowable torque of the shift clutch after the start of hydraulic control by the lockup clutch control means until the lockup clutch is completely engaged. The slip state of the transmission clutch may be controlled so as to match the torque of the turbine at the start of the control of.

Further, in the control device of the transmission, after the lockup clutch is completely engaged, the torque of the drive source is temporarily reduced from the torque required by the driver, and then the torque of the drive source is reduced to the torque required by the driver. It may be further provided with a drive source control means for controlling the rotation speed of the turbine and the rotation speed of the input shaft of the transmission mechanism in synchronization with each other.

Further, in the control device of the transmission, after the lockup clutch is completely engaged, the allowable torque of the transmission clutch is temporarily increased, and then the allowable torque is changed to the driver required torque to obtain the turbine. A synchronization control means for controlling the rotation speed of the speed change mechanism and the rotation speed of the input shaft of the transmission mechanism may be further provided.

According to the present invention, when establishing a drive force transmission path from a drive source to a drive wheel via a lockup clutch, the occurrence of a shock can be reduced and the drive force transmission path can be quickly set. Can be established.

It is a schematic block diagram which shows the transmission which concerns on one Embodiment of this invention. It is a figure which shows the symbol which represents the state value of the model which corresponds to the transmission which concerns on one Embodiment of this invention, and each part of a transmission. It is a flowchart of the lock-up clutch engagement process which concerns on one Embodiment of this invention. FIG. 4A is a diagram showing a time change of the rotation speed of each part in each phase of the lockup clutch engagement process according to the embodiment of the present invention. FIG. 4B is a diagram showing a time change of torque of each part in each phase of the lockup clutch engagement process according to the embodiment of the present invention. It is a flowchart of the lock-up clutch engagement process which concerns on the modification of this invention. FIG. 6A is a diagram showing a time change of the rotation speed of each part in each phase of the lockup clutch engagement process according to the modified example of the present invention. FIG. 6B is a diagram showing a time change of torque of each part in each phase of the lockup clutch engagement process according to the modified example of the present invention.

Hereinafter, a transmission control device according to an embodiment of the present invention will be described with reference to the accompanying drawings. The same parts have the same reference numerals, and their names and functions are also the same. Therefore, detailed explanations about them will not be repeated.

FIG. 1 is a schematic configuration diagram showing a transmission according to an embodiment of the present invention.

The transmission 1 provided in the vehicle is connected to the output shaft 11 of the engine 10, which is an example of a drive source.

The transmission 1 includes a torque converter (torque converter) 12, a speed change clutch 20, a speed change mechanism 30, a control device 2, a torque converter hydraulic oil adjustment unit 85, a clutch hydraulic oil adjustment unit 86, and a speed change adjustment unit 87. The engine rotation speed sensor 92, the turbine rotation speed sensor 93, the input shaft rotation speed sensor 94, the vehicle speed sensor 95 (also referred to as the output rotation speed sensor), the accelerator opening sensor 96, and the shift position sensor 97. I have. The control device 2 includes an engine electronic control device (engine ECU) 70 and a transmission electronic control device (transmission ECU) 80.

Here, before explaining the details of the transmission 1, the model corresponding to the transmission 1 and the symbols representing the state values of each part of the transmission 1 will be described.

FIG. 2 is a diagram showing a model corresponding to the transmission according to the embodiment of the present invention and symbols representing state values of each part of the transmission.

The part related to the control of the transmission 1 shown in FIG. 1 can be represented as in the model shown in FIG. In the present specification, the state value indicating the state of each part of the transmission 1 is represented by a symbol or a subscripted symbol as shown in FIG.

Here, the symbols will be described. T represents torque, ω represents the number of revolutions, I represents the moment of inertia, and i represents the gear ratio. On the other hand, to explain the subscripts attached to the symbols, e represents an engine, lck represents a lockup clutch, i represents an impeller, t represents a turbine shaft, and c represents a transmission clutch. o represents the output shaft of the transmission mechanism, and l represents the load on the drive wheel side.

Returning to the description of FIG. 1, the torque converter 12 includes an impeller 13 connected to the output shaft 11 of the engine 10 and a turbine 14 arranged so as to face the impeller 13 and connected to the input shaft 19 of the speed change clutch 20. The lock-up clutch 15 is capable of mechanically engaging and disengaging between the output shaft 11 and the input shaft 19 (turbine shaft).

The lockup clutch 15 is provided in a predetermined direction (left-right direction in the drawing) with the input side clutch disc 15B provided so as to be integrally rotatable with the output shaft 11 and the output side clutch disc 15C provided so as to be integrally rotatable with the input shaft 19. It has a piston 15A that can move and press the input side clutch disc 15B and the output side clutch disc 15C to press-contact the input side clutch disc 15B and the output side clutch disc 15C. The piston 15A has a locking force of the lockup clutch 15, that is, an input side clutch disc 15B and an output side clutch disc 15C, according to the hydraulic pressure supplied from the torque converter hydraulic oil adjusting unit 85 to the adjacent hydraulic oil chamber 16. It is possible to adjust the fastening force between them. The movement of the piston 15A of the present embodiment can be adjusted by the hydraulic pressure of the hydraulic oil chamber 16, and is not affected by the pressure of the hydraulic oil in the circulation hydraulic chamber 17 around the impeller 13 and the turbine 14. Therefore, since the movement of the piston 15A can be controlled quickly and with high accuracy, the fastening force of the lockup clutch 15 can be controlled quickly and with high accuracy.

Here, in the present embodiment, the state in which the torque from the output shaft 11 is transmitted to the input shaft 19 is completely satisfied while the input side clutch disk 15B and the output side clutch disk 15C are in contact with each other and rotate at the same rotation speed. The locked-up clutch 15 refers to a state in which the torque from the output shaft 11 is transmitted to the input shaft 19 while the input side clutch disc 15B and the output side clutch disc 15C are in contact with each other and rotate at different rotation speeds. The slip state (half-clutch state) is referred to, and the state in which the input side clutch disc 15B and the output side clutch disc 15C are not in contact is referred to as a disengagement state of the lockup clutch 15.

The speed change clutch 20 is, for example, a wet clutch, and is an input side disk 20A that rotates integrally with an input shaft 19 connected to a turbine 14 of a torque converter 12, and an output side disk that rotates integrally with an input shaft 31 of a transmission 30. It has 20B, and can connect and disconnect the driving force between the input side disk 20A and the output side disk 20B. The fastening force of the speed change clutch 20, that is, the fastening force between the input side disc 20A and the output disc 20B can be adjusted by the pressure of the hydraulic oil supplied from the clutch hydraulic oil adjusting unit 86.

Here, in the present embodiment, the input side disk 20A and the output side disk 20B are in contact with each other and rotate at the same rotation speed, and the torque is completely transmitted from the input side disk 20A to the output side disk 20B. The state in which torque is transmitted from the input side disc 20A to the output side disc 20B while the input side disc 20A and the output side disc 20B rotate at different rotation speeds is called a state, which is a slip state of the speed change clutch 20 (half-clutch state). ), And the state in which the input side disc 20A and the output side disc 20B are not in mechanical contact is referred to as a disengaged state of the speed change clutch 20.

The transmission mechanism 30 shifts the driving force input from the input shaft 31 connected to the output side disk 20B of the transmission clutch 20 and transmits the driving force to the output shaft 32 connected to the drive wheels (not shown). The transmission mechanism 30 may be, for example, a parallel shaft gear type transmission mechanism (that is, a manual transmission), a planetary gear type transmission mechanism, or a continuously variable transmission mechanism.

The torque converter hydraulic oil adjusting unit 85 adjusts the pressure of the hydraulic oil supplied to the hydraulic chamber 16 of the torque converter 12 according to the control instruction of the transmission ECU 80. In the present embodiment, the torque converter hydraulic oil adjusting unit 85 can switch the flow path of the hydraulic oil between the hydraulic oil supply source and the hydraulic chamber 16 (not shown) between an on state (open state) and an off state (closed state). When the on / off valve 85A is provided and the oil pressure of the hydraulic chamber 16 is raised, the on / off valve 85A is adjusted to be in the on state. The on / off valve 85A has an advantage that the cost is lower than that of the solenoid valve whose flow rate can be finely adjusted. Further, the torque converter hydraulic oil adjusting unit 85 adjusts the flow rate and pressure of the hydraulic oil supplied to the circulation hydraulic chamber 17 of the torque converter 12 according to the control instruction of the transmission ECU 80.

The clutch hydraulic oil adjusting unit 86 adjusts the pressure of the hydraulic oil supplied to the shifting clutch 20 in order to adjust the fastening force of the shifting clutch 20 according to the control instruction of the transmission ECU 80.

The speed change adjusting unit 87 changes the speed change stage of the speed change mechanism 30 according to the control instruction of the transmission ECU 80.

The engine speed sensor 92 detects the speed of the output shaft 11 of the engine 10 (engine speed ω _e ) and outputs it to the engine ECU 70. The turbine rotation speed sensor 93 detects the rotation speed of the input shaft 19 ( _{corresponding to the rotation speed of the turbine 14 (turbine rotation speed ω t} )) and outputs it to the transmission ECU 80. The input shaft rotation speed sensor 94 detects the rotation speed of the input shaft 31 (input shaft rotation speed ω _c ) and outputs it to the transmission ECU 80. The vehicle speed sensor 95 detects the rotation speed of the output shaft 32 (output shaft rotation speed ω _o ) and outputs it to the transmission ECU 80. The vehicle speed can be specified from the output shaft rotation speed ω _o. The accelerator opening sensor 96 detects the accelerator opening and outputs it to the engine ECU 70. The shift position sensor 97 detects a position (shift position) designated (selected) by the operation lever and outputs the position (shift position) to the transmission ECU 80. With the operating lever, for example, the P (parking) range used when the vehicle is stopped, the N (neutral) range selected when the vehicle's transmission is set to neutral, and the D (drive) range selected when performing automatic shifting. , M (manual) range selected when shifting is performed by the driver's operation, plus (+) to specify upshift in M range, minus (-) to specify downshift in M range Etc. can be selected.

The engine ECU 70 mainly performs various controls of the engine 10, and is configured to include a known CPU, ROM, RAM, input port, output port, and the like. In order to perform these various controls, sensor values of various sensors (92, 96) are input to the engine ECU 70. The engine ECU 70 is connected to the transmission ECU 80 via a communication network so that various information can be exchanged with each other.

The engine ECU 70 has an engine control unit 71 as an example of a drive source control means as a part of a functional element.

The engine control unit 71 controls the torque of the engine 10 by controlling the fuel injection amount and the like in the engine 10. For example, the engine control unit 71 is assumed to be requested by the driver for the engine 10 based on the accelerator opening degree from the accelerator opening degree sensor 96 and the vehicle speed (for example, acquired from the transmission ECU 80). The required engine torque T _ed (driver required torque) is determined and output to the transmission ECU 80. Further, the engine control unit 71 temporarily reduces _{the torque of the engine 10 (engine torque Te} ) from the driver required engine torque T _ed after the lockup clutch 15 is completely engaged, and then the engine control unit 71 temporarily reduces the torque (engine torque Te) of the engine 10 from the driver required engine torque T ed. The engine torque T _e is changed to the driver required engine torque T _ed , and the turbine rotation speed ω _t and the input shaft rotation speed ω _c are controlled to be synchronized.

The transmission ECU 80 mainly controls various types of the torque converter 12, the transmission clutch 20, and the transmission mechanism 30, and includes a known CPU, ROM, RAM, input port, output port, and the like. In order to perform these various controls, sensor values of various sensors (93 to 95, 97) are input to the transmission ECU 80.

The transmission ECU 80 includes a general control unit 81 as an example of the start determination means, a torque converter control unit 82 as an example of the lockup clutch control means, and a clutch control as an example of the first clutch control means and the second clutch control means. A unit 83 and a shift control unit 84 are included as some functional elements.

In the present embodiment, the engine ECU 70 and the transmission ECU 80 are configured as separate hardware, but the engine ECU 70 and the transmission ECU 80 may be configured as integrated hardware. Further, the functional elements of the engine ECU 70 and the functional elements of the transmission ECU 80 may be distributed and provided in two or more hardwares.

The overall control unit 81 controls the process of engaging the lockup clutch 15 to establish the transmission path of the driving force from the engine 10 to the drive wheels (lockup clutch engagement process). The overall control unit 81 determines whether or not a predetermined condition for engaging the lockup clutch 15 of the torque converter 12 is satisfied, and if the predetermined condition is satisfied, notifies the clutch control unit 83 to that effect. As a predetermined condition for engaging the lockup clutch 15, for example, the engine speed ω _e is higher than the rotation speed at which the damper (not shown) of the torque converter 12 resonates when the lockup clutch 15 is engaged. It may be that it became. Other processes executed by the overall control unit 81 will be described later.

Torque converter control unit 82, when the allowable torque T _c matches the turbine torque T _t (if the allowable torque T _c from the clutch control unit 83 receives a notification that matched the turbine torque T _t), the lock-up clutch By turning on the on / off valve 85A of the torque converter hydraulic oil adjusting unit 85 so as to fasten 15, the control of the hydraulic oil hydraulic pressure to the hydraulic chamber 16 is started. Here, the time when the torque converter hydraulic oil adjusting unit 85 starts controlling the hydraulic oil of the hydraulic oil to the hydraulic chamber 16 so as to engage the lockup clutch 15 is defined as the lockup hydraulic control start time. Other processes executed by the torque converter control unit 82 will be described later.

When the clutch control unit 83 receives a notification from the general control unit 81 that the predetermined condition for engaging the lockup clutch 15 of the torque converter 12 is satisfied, the shift clutch 20 is put into a slip state and the allowable torque of the shift clutch 20 is set. T _c is controlled so as to match the turbine torque T _t. Here, regarding the allowable torque T _c , the oil pressure of the hydraulic oil supplied by the clutch hydraulic oil adjusting unit 86 in the speed change clutch 20 and the permissible torque T _{c of the speed change clutch 20 which are experimentally grasped in advance.} From information that can identify the oil pressure of the hydraulic oil supplied from the clutch hydraulic oil adjusting unit 86 (the hydraulic oil pressure itself, or the amount of current that controls the valve that adjusts the hydraulic pressure, etc.) Can be identified. The turbine torque T _{t is determined by the torque ratio tr corresponding to the speed ratio between the engine speed ω e} and the turbine speed ω _t in the torque converter 12 and the design of the torque converter 12 which are known in advance. It can be specified by using the pump capacity coefficient C and the engine speed ω _{e detected from the sensor.} More specifically, the turbine torque T _t can be specified by T _t = tr × C × ω _e ^2.

The clutch control unit 83 determines whether or not the allowable torque T _c matches the turbine torque T _t, when the allowable torque T _c matches the turbine torque T _t is the fact to the torque converter control unit 82 Notice.

Further, in the clutch control unit 83, after the start of the lockup hydraulic control, at least _{until a difference occurs between the turbine rotation speed ω t} and the input shaft rotation speed ω _c (for example, until the lockup clutch 15 is completely engaged). ), The allowable torque T _c of the speed change clutch 20 is supplied to the speed change clutch 20 by the clutch hydraulic oil adjusting unit 86 so as to match _{the turbine torque T t} (target clutch torque T _FLU ) at the start of lockup hydraulic control. The slip state of the speed change clutch 20 is controlled by adjusting the hydraulic pressure of the hydraulic oil. In the present embodiment, the target clutch torque T _{FLU , which is the turbine torque T t} at the start of lockup hydraulic control, is lower than the driver required engine torque T _ed. Other processes executed by the clutch control unit 83 will be described later.

The shift control unit 84 determines whether or not shift is required based on information such as a designated position of the operation lever transmitted from the shift position sensor 97, an accelerator opening degree (obtained from the engine ECU 70), and a vehicle speed from the vehicle speed sensor 95. If a shift is required, the shift destination is specified, and a control instruction is output to the shift adjustment unit 87 so as to set the shift mechanism 30 to that shift.

Next, the lockup clutch engagement process in the transmission 1 will be described. The lockup clutch engagement process is a process for establishing a driving force transmission path from the engine 10 to the drive wheels, which involves locking up (completely engaging) the lockup clutch 15.

FIG. 3 is a flowchart of the lockup clutch engagement process according to the embodiment of the present invention. FIG. 4A is a diagram showing a time change of the rotation speed of each part in each phase of the lockup clutch engagement process according to the embodiment of the present invention. FIG. 4B is a diagram showing a time change of torque of each part in each phase of the lockup clutch engagement process according to the embodiment of the present invention. Note that the time axes 1, 2, ... In FIG. 4 indicate control phase 1, control phase 2, ....

The lockup clutch engagement process is executed when the lockup clutch 15 of the torque converter 12 is not engaged, for example, immediately after the vehicle starts, or when the speed of the vehicle decreases. The initial state in the lockup clutch engagement process is the pre-control phase in the control phase, and in the pre-control phase, the speed change clutch 20 is in a completely engaged state.

In the pre-control phase, the lockup clutch 15 of the torque converter 12 is disconnected and the speed change clutch 20 is completely engaged. In the phase before the start of control, the equation of motion in the transmission 1 can be expressed by the following equations (1), (2), and (3).

ここで、制御開始前フェーズにおいて、ドライバによりアクセルが踏まれてアクセル開度が大きくなった場合を例にして、ロックアップクラッチ締結処理の各ステップを説明する。制御開始前フェーズにおいて、アクセル開度が大きくなると、図４（Ａ）及び図（Ｂ）に示すように、ドライバ要求エンジントルクＴ_ｅｄが高くなり、エンジントルクＴ_ｅが高くなるように制御される。この結果、タービントルクＴ_ｔが上昇し、エンジン回転数ω_ｅ、インプットシャフト回転数ω_ｃが上昇する。なお、本実施形態では、ドライバ要求エンジントルクＴ_ｅｄが高くなって所定の値で一定となるようにアクセル開度が維持されている場合を例に説明する。

Here, each step of the lockup clutch engagement process will be described by taking as an example a case where the accelerator is stepped on by the driver and the accelerator opening is increased in the phase before the start of control. In the phase before the start of control, when the accelerator opening becomes large, the driver-required engine torque T _ed becomes high and the engine torque T _e becomes high, as shown in FIGS. 4A and 4B. .. As a result, the turbine torque _Tt increases, and the engine speed ω _e and the input shaft speed ω _c increase. In this embodiment, a case where the accelerator opening degree is maintained so that the driver-required engine torque T _ed becomes high and becomes constant at a predetermined value will be described as an example.

The general control unit 81 performs a predetermined rotation in which the lockup clutch 15 of the torque converter 12 is engaged (for example, the engine speed ω _e is higher than the rotation speed at which the damper (not shown) of the torque converter 12 resonates. It is determined whether or not it satisfies (which is a number) (step S11). As a result, when the predetermined condition is not satisfied (step S11: NO), the phase before the start of control remains, so that the overall control unit 81 executes step S11 again.

On the other hand, when a predetermined condition is satisfied (step S11: YES), the control phase shifts from the pre-control phase to the control phase 1, and the overall control unit 81 informs the clutch control unit 83 that the predetermined condition is satisfied. Notice.

Upon receiving the notification that the predetermined condition is satisfied, the clutch control unit 83 puts the speed change clutch 20 in a slip state and starts control so that _{the allowable torque T c} of the speed change clutch 20 matches the turbine torque T _{t (.} Step S12).

In the control phase 1, the lockup clutch 15 of the torque converter 12 is in the disconnected state and the speed change clutch 20 is in the slip state. Therefore, the equations of motion in the transmission 1 are the equations (1), (2), and (1). It can be represented by 3).

In the control phase 1, the allowable torque T _c is controlled so as to match the turbine torque T _t . Therefore, as shown in FIG. 4 (B), the allowable torque T _c gradually decreases to the turbine torque. It will be closer to T _t.

Then, the clutch control unit 83 determines whether or not the allowable torque _{T c} matches the turbine torque _{T t} (step S13), and if the allowable torque _{T c} is not coincident with the turbine torque _{T t} (step S13: NO ), Since the control phase 1 remains, the clutch control unit 83 executes step S13 again.

On the other hand, when the allowable torque T _c matches the turbine torque T _t (step S13: YES), the control phase shifts to the control phase 2, and the clutch control unit 83 notifies the torque converter control unit 82 to that effect. ..

When the torque converter control unit 82 receives a notification from the clutch control unit 83 that the allowable torque T _c matches the turbine torque T _t , the torque converter control unit 82 starts locking up the lockup clutch 15, that is, the lockup clutch 15 By turning on the on / off valve 85A of the torque converter hydraulic oil adjusting unit 85 so as to fasten the clutch, the control of the hydraulic oil pressure to the hydraulic chamber 16 is started (step S14). At this point, the lockup hydraulic control is started. As a result, the torque that can be transmitted by the lockup clutch 15 (lockup clutch allowable torque T _ck ) gradually increases. The lockup clutch allowable torque T _ck is determined by the oil pressure supplied by the torque converter hydraulic oil adjusting unit 85, and the oil pressure in the hydraulic chamber 16 rises relatively early. Therefore, it is shown in FIG. 4 (B). It rises relatively early.

Next, the control phase shifts to the control phase 3, and the clutch control unit 83 makes the allowable torque T _c of the speed change clutch 20 match _{the turbine torque T t} (target clutch torque T _FLU ) at the start of the lockup hydraulic control. In addition, control of the slip state of the speed change clutch 20 is started by adjusting the hydraulic pressure of the hydraulic oil supplied to the speed change clutch 20 by the clutch hydraulic oil adjusting unit 86 (step S15). Here, the target clutch torque T _FLU is lower than the driver required engine torque T _ed. Therefore, since a large change in torque does not occur on the rear stage side of the speed change clutch 20, a _{large shock does not occur even if the lockup clutch allowable torque T ck} increases, so that the occurrence of a shock can be reduced. Further, since the allowable torque T _c is controlled so as to match the _{target clutch torque T FLU} , which is a constant value, instead of the _{turbine torque T t} , which is greatly reduced by the turbine rotation speed ω _{t, the speed change clutch 20} It is possible to prevent the torque on the rear stage side from being greatly reduced.

In the control phase 2 and the control phase 3, the lockup clutch 15 of the torque converter 12 is in the slip state and the speed change clutch 20 is in the slip state. Therefore, the equations of motion in the transmission 1 are the equations (4) and (5). ), And can be expressed by the equation (3).

次いで、統括制御部８１は、タービン回転数ω_ｔがインプットシャフト回転数ω_ｃよりも高い回転数となったか否かを判定し（ステップＳ１６）、タービン回転数ω_ｔがインプットシャフト回転数ω_ｃよりも高い回転数でない場合（ステップＳ１６：ＮＯ）には、制御フェーズ３のままであるので、統括制御部８１は、ステップＳ１６を再び実行する。

Then, the central control unit 81, turbine speed omega _t is determined whether or not a rotational speed higher than the input shaft rotational speed omega _c (step S16), and the turbine rotational speed omega _t is the input shaft rotational speed omega _c If the rotation speed is not higher than (step S16: NO), the control phase 3 remains, so that the general control unit 81 executes step S16 again.

On the other hand, when the turbine rotation speed ω _t becomes higher than the input shaft rotation speed ω _c (step S16: YES), the control phase shifts to the control phase 4, and the integrated control unit 81 rotates the turbine. The engine control unit 71 is notified that the number ω _t is higher than the input shaft rotation speed ω _c.

The engine control unit 71 to the turbine rotational speed omega _t has received to the effect that a higher rotational speed than the input shaft rotational speed omega _c is controlled to the engine torque T _e is consistent with impeller torque T _i (step S17) .. Impeller torque _{T i can} be estimated by ^{_{T i = C × ω e 2}} . Here, the coefficient C is the pump capacitance coefficient of the torque converter 12, and is a value determined by the design value of the torque converter 12.

At the time of step S17, the clutch control unit 83 continuously executes the control to make _{the allowable torque T c} of the speed change clutch 20 match the target clutch torque T _FLU. Therefore, since a large torque change does not occur on the rear stage side of the speed change clutch 20, a _{large shock does not occur even if the lockup clutch allowable torque T ck} increases, and the occurrence of a shock can be reduced. ..

In the control phase 4, the lockup clutch 15 of the torque converter 12 is in the slip state, and the speed change clutch 20 is in the slip state. Therefore, the equations of motion in the transmission 1 are the equations (4), (6), and (1). It can be represented by 7).

制御フェーズ４においては、タービントルクＴ_ｔは、徐々に減少していき、タービン回転数ω_ｔがエンジン回転数ω_ｅに近づくように増加する。

In the control phase 4, the turbine torque T _t gradually decreases and increases so that the turbine speed ω _t approaches the engine speed ω _e.

Then, the central control unit 81, turbine speed omega _t is determined whether or not a same rotational speed as the engine speed omega _e (step S18), and the turbine rotational speed omega _t the same speed as the engine rotation speed omega _e If it is not a number (step S18: NO), the control phase 4 remains, so that the general control unit 81 executes step S18 again.

On the other hand, when the turbine speed ω _t becomes the same speed as the engine speed ω _e (step S18: YES), it is considered that the lockup clutch 15 has been completely engaged, so that the control phase is set to Moving to the control phase 5, the integrated control unit 81 notifies the engine control unit 71 and the clutch control unit 83 that _{the turbine speed ω t} has become the same speed as the engine speed ω _e.

The engine control unit 71, the engine torque T _e is temporarily reduced from the driver required engine torque T _ed, then, by varying the engine torque T _e to the driver required engine torque T _ed, and the turbine rotational speed omega _t, It is controlled to synchronize with the input shaft rotation speed ω _c. In the present embodiment, the engine control unit 71 controls so as to satisfy the equation (8) (step S19). In addition, ω^・ _ec (in the formula (8), one dot (・) above ω, in the specification, it is expressed as such for convenience) indicates a preset target value of the engine rotation angular velocity. This is a value corresponding to the rate of decrease in the _{engine speed ω e} shown in FIG. 4 (A). Since the engine torque _Te is temporarily reduced in this way, the turbine rotation speed ω _t and the input shaft rotation speed ω _c can be rapidly synchronized.

また、クラッチ制御部８３は、変速クラッチ２０の許容トルクＴ_ｃを、ドライバ要求エンジントルクＴ_ｅｄと一致させるように上昇させる（ステップＳ１９）。ここで、上記したように、エンジントルクＴ_ｅを一時的に低下させるので、変速クラッチ２０の許容トルクＴ_ｃを、ドライバ要求エンジントルクＴ_ｅｄと一致させるように上昇させる際におけるショックの発生を抑えることができる。

Further, the clutch control unit 83 _{raises the allowable torque T c} of the speed change clutch 20 so as to match the driver required engine torque T _{ed (step S19).} Here, as described above, since the engine torque _Te is temporarily lowered, it is possible to suppress the occurrence of a shock when raising _{the allowable torque T c} of the speed change clutch 20 so as to match the driver required engine torque T _ed. be able to.

In the control phase 5, the lockup clutch 15 of the torque converter 12 is completely engaged and the transmission clutch 20 is in the slip state. Therefore, the equations of motion in the transmission 1 are equations (9) and (7). ) Can be expressed.

制御フェーズ５においては、エンジントルクＴ_ｅがドライバ要求エンジントルクＴ_ｅｄよりも一時的に減少し、その後、ドライバ要求エンジントルクＴ_ｅｄに一致する。また、許容トルクＴ_ｃは、徐々に上昇していき、ドライバ要求エンジントルクＴ_ｅｄと一致する。また、エンジン回転数ω_ｅ（タービン回転数ω_ｔと同じ）は、低下していきインプットシャフト回転数ω_ｃに徐々に近づく。

In the control phase 5, the engine torque T _e is decreased temporarily than the driver required engine torque T _ed, then match the driver required engine torque T _ed. Further, the allowable torque T _c gradually increases and coincides with the driver required engine torque T _ed. Further, the engine speed ω _e (same as the turbine speed ω _t ) gradually decreases and gradually approaches the input shaft speed ω _c.

Next, the general control unit 81 _{determines whether or not the rotation speed difference between the engine speed ω e} and the input shaft speed ω _c is smaller than a predetermined value (step S20), and the engine speed ω _e and the input If the rotation speed difference from the shaft rotation speed ω _c is not smaller than the predetermined value (step S20: NO), the control phase 5 remains, so that the general control unit 81 executes step S20 again. ..

On the other hand, _{when the rotation speed difference between the engine speed ω e} and the input shaft speed ω _c becomes smaller than a predetermined value (step S20: YES), even if the speed change clutch 20 is completely engaged, when it is engaged. Since it is considered that the shock is relatively small, the control phase shifts to the control phase 6, and the general control unit 81 has _{a rotation speed difference between the engine speed ω e} and the input shaft speed ω _c smaller than the predetermined value. Notify the clutch control unit 83 of the fact.

Upon receiving the notification, the clutch control unit 83 adjusts the hydraulic pressure of the hydraulic oil supplied to the transmission clutch 20 by the clutch hydraulic oil adjustment unit 86, so that the transmission clutch 20 completely _{adjusts the allowable torque Tc of the transmission clutch 20. It is adjusted} to match the torque at the time of fastening (torque at the time of complete fastening T MAX) (step S21).

Then, the central control unit 81, the allowable torque _{T c} of the shift clutch 20, it is determined whether or not consistent with the full engagement when the torque _{T MAX} (step S22), and the allowable torque _{T c} of the shift clutch 20, full engagement If the hour torque _{does not match T MAX} (step S22: NO), the speed change clutch 20 is not completely engaged and remains in the control phase 6, so that the general control unit 81 again performs step S22. Execute.

On the other hand, when the allowable torque T _{c of the speed change clutch 20 matches the torque T MAX} at the time of complete engagement (step S22: YES), it means that the speed change clutch 20 is completely engaged, and the torque converter 12 is locked. Since it means that the driving force transmission path from the engine 10 to the driving wheels via the up clutch 15 has been completely established, the general control unit 81 returns the engine control unit 71 to the normal control state. The lockup clutch engagement process is completed.

As described above, according to the control device 2 according to the present embodiment, the lockup clutch 15 is a hydraulic chamber on one side of the piston 15A that presses the input side clutch disk 15B and the output side clutch disk 15C of the lockup clutch 15. The fastening force can be adjusted by the hydraulic pressure of the hydraulic oil supplied to 16, and the general control unit 81 determines whether or not the predetermined condition for engaging the lockup clutch 15 of the torque converter 12 is satisfied, and the clutch control unit 83 determines whether or not the condition is satisfied. When it is determined that the predetermined condition is satisfied, the speed change clutch 20 is put into a slip state, and the allowable torque T _c that can be transmitted by the speed change clutch 20 is controlled so as to match the turbine torque T _t. However, when the permissible torque T _c matches the turbine torque T _t , the control of the hydraulic oil of the hydraulic fluid in the hydraulic chamber 16 is started so as to engage the lockup clutch 15, and the clutch control unit 83 further controls the clutch. After the start of hydraulic control by the unit 82, _{the allowable torque T c} of the speed change clutch 20 is set to _{the turbine torque T t} at the start of hydraulic control _{until at least a difference occurs between the turbine rotation speed ω t} and the input shaft rotation speed ω _c. Since the slip state of the speed change clutch 20 is controlled so as to match the target clutch torque T _FLU , the speed change clutch 20 is used when establishing a drive force transmission path accompanied by lockup of the lockup clutch. It is possible to reduce the transmission of a relatively large torque to the rear stage side, and it is possible to reduce the occurrence of a shock. Further, since the fastening force of the lockup clutch 15 can be adjusted by supplying hydraulic oil to the hydraulic chamber 16, the time required to completely engage the lockup clutch 15 can be shortened, and as a result, the lockup clutch 15 can be engaged. It is possible to quickly establish a transmission path for driving force accompanied by lockup.

Next, the transmission 1 according to the modified example will be described. The same parts as those of the transmission according to the above-described embodiment are designated by the same reference numerals, and the differences will be mainly described.

The clutch control unit 83 of the transmission 1 according to the modified example is an example of the synchronous control means, and is supplied to the speed change clutch 20 by the clutch hydraulic oil adjusting unit 86 after the lockup clutch 15 is completely engaged. By adjusting the hydraulic pressure of the hydraulic oil, the allowable torque T _c of the transmission clutch 20 is temporarily increased, and then the allowable torque T _c is changed to the driver required engine torque T _ed to obtain the turbine rotation speed ω _t . , Control to synchronize with the input shaft rotation speed ω _c.

Next, the lockup clutch engagement process in the transmission 1 according to the modified example will be described.

FIG. 5 is a flowchart of the lockup clutch engagement process according to the modified example of the present invention. FIG. 6A is a diagram showing a time change of the rotation speed of each part in each phase of the lockup clutch engagement process according to the modified example of the present invention. FIG. 6B is a diagram showing a time change of torque of each part in each phase of the lockup clutch engagement process according to the modified example of the present invention. Note that the time axes 1, 2, ... In FIG. 6 indicate control phase 1, control phase 2, ....

In step S20, when the turbine speed ω _t becomes the same speed as the engine speed ω _e (step S18: YES), it is considered that the lockup clutch 15 has been completely engaged, so that the control phase Moves to the control phase 5, and the integrated control unit 81 notifies the clutch control unit 83 that _{the turbine speed ω t} has become the same speed as the engine speed ω _e. Here, since the integrated control unit 81 and the clutch control unit 83 are provided in the transmission ECU 80, it is possible to promptly notify the clutch control unit 83 to that effect without being affected by the delay due to communication.

_{The clutch control unit 83 temporarily increases the allowable torque T c} of the speed change clutch 20, and then changes the allowable torque T _c to the driver required engine torque T _ed to obtain the turbine rotation speed ω _t and the input shaft rotation speed. Control to synchronize with ω _c. In the present embodiment, the clutch control unit 83 controls so as to satisfy the equation (10) (step S23).

なお、ω^・ _ｅｃ（式（１０）では、ωの上に１つのドット（・）、明細書では便宜的にこの様に表記する）は、予め設定されたエンジン回転角速度の目標値を示しており、図６（Ａ）に示すエンジン回転数ω_ｅの低下速度に相当する値となっている。このように、許容トルクＴ_ｃを一時的に増加させるので、タービン回転数ω_ｔと、インプットシャフト回転数ω_ｃとを迅速に同期させることができる。ここで、タービン回転数ω_ｔと、インプットシャフト回転数ω_ｃとを同期するためには、例えば、エンジン１０のトルクを制御することも考えられるが、本実施形態では、エンジン１０のトルク制御よりも応答遅れが少ない変速クラッチ２０の許容トルクＴ_ｃを制御するようにしているので、タービン回転数ω_ｔと、インプットシャフト回転数ω_ｃとをより早期に同期させることができるとともに、その際に発生するショックの発生を効果的に低減することができる。

In addition, ω^・ _ec (in the formula (10), one dot (・) above ω, in the specification, it is expressed as such for convenience) indicates a preset target value of the engine rotation angular velocity. This is a value corresponding to the rate of decrease in the _{engine speed ω e} shown in FIG. 6 (A). In this way, since the allowable torque T _c is temporarily increased, the turbine rotation speed ω _t and the input shaft rotation speed ω _c can be rapidly synchronized. Here, in order to synchronize the turbine rotation speed ω _t and the input shaft rotation speed ω _c , for example, it is conceivable to control the torque of the engine 10, but in the present embodiment, the torque control of the engine 10 is used. _{Since the allowable torque T c} of the speed change clutch 20 with less response delay is controlled, the turbine rotation speed ω _t and the input shaft rotation speed ω _c can be synchronized earlier, and at that time, The occurrence of the generated shock can be effectively reduced.

As described above, according to the control device 2 according to the modified example, the clutch control unit 83 temporarily increases _{the allowable torque Tc of the speed change clutch 20 after the lockup clutch 15 is completely engaged.} After that, the allowable torque T _c was changed to the driver required engine torque T _ed to control the turbine rotation speed ω _t and the input shaft rotation speed ω _{c of the} transmission mechanism 30 in synchronization with each other. The transmission path of the driving force accompanied by the lockup of the up clutch 15 can be quickly established.

The present invention is not limited to the above-described embodiment, and can be appropriately modified and implemented without departing from the spirit of the present invention.

For example, in the above embodiment, the target clutch torque T _FLU is lower than the driver required engine torque T _ed , but the present invention is not limited to this, and the torque is the same as the _{driver required engine torque T ed.} May be good.

Further, in the above embodiment, the engine 10 has been given as an example as a drive source, but the present invention is not limited to this. For example, the drive source may be an electric motor, and the drive source may be an engine and an electric motor. It may be a combination.

1 Transmission 2 Control device 10 Engine 11 Output shaft 12 Torque converter 13 Impeller 14 Turbine 15 Lockup clutch 15A Piston 15B Input side clutch plate 15C Output side clutch plate 16 Hydraulic chamber 17 Circulation hydraulic chamber 19 Input shaft 20 Speed change clutch 30 Mechanism 70 Engine ECU
71 Engine control unit 80 Transmission ECU
81 General control unit 82 Torque converter control unit 83 Clutch control unit 84 Shift control unit 85 Torque converter hydraulic oil adjustment unit 85A On / off valve 86 Clutch hydraulic oil adjustment unit 87 Shift adjustment unit 92 Engine rotation speed sensor 93 Turbine rotation speed sensor 94 Input shaft Rotation speed sensor 95 Vehicle speed sensor 96 Accelerator opening sensor 97 Shift position sensor

Claims (5)

It has a transmission mechanism, an impeller provided between the drive source and the transmission mechanism and connected to the drive source side, and a turbine connected to the transmission mechanism side, and the impeller and the impeller via hydraulic oil. A torque converter having a lockup clutch capable of transmitting power to and from the turbine and mechanically connecting the drive source side and the turbine to control power transmission, and the torque. A transmission control device having a speed change clutch arranged between the converter and the speed change mechanism and capable of controlling power transmission between the torque converter and the speed change mechanism.
The locking force of the lockup clutch can be adjusted by the hydraulic pressure of the hydraulic oil supplied to the hydraulic chamber on one side of the piston that presses the clutch disc of the lockup clutch.
A start determining means for determining whether or not a predetermined condition for engaging the lockup clutch of the torque converter is satisfied, and
When the start determination means determines that a predetermined condition is satisfied, the first clutch controls the shift clutch so that the allowable torque that can be transmitted by the shift clutch matches the torque of the turbine, with the shift clutch in a slip state. Control means and
A lockup clutch control means that starts control of the hydraulic pressure of the hydraulic oil to the hydraulic chamber so as to engage the lockup clutch when the allowable torque matches the torque of the turbine.
After the start of the control of the hydraulic pressure by the lockup clutch control means, the allowable torque of the shift clutch is applied to the hydraulic pressure until at least a difference occurs between the rotation speed of the turbine and the rotation speed of the input shaft of the transmission mechanism. A second clutch control means that controls the slip state of the speed change clutch so as to match the torque of the turbine at the start of control.
Transmission control device. When the allowable torque matches the torque of the turbine, the lockup clutch control means enters the hydraulic chamber by turning on the on / off valve between the hydraulic chamber and the hydraulic oil supply source. The control device for a transmission according to claim 1, wherein the control of the hydraulic pressure supply of the hydraulic oil is started. The transmission according to claim 1 or 2, wherein the torque of the turbine at the start of the control of the hydraulic pressure is less than or equal to the torque required by the driver for the drive source. Control device. After the start of the control of the hydraulic pressure by the lockup clutch control means, the second clutch control means controls the hydraulic pressure by controlling the allowable torque of the transmission clutch until the lockup clutch is completely engaged. The transmission control device according to any one of claims 1 to 3, which controls the slip state of the transmission clutch so as to match the torque of the turbine at the start time. After the lockup clutch is completely engaged, the torque of the drive source is temporarily reduced from the torque required by the driver, and then the torque of the drive source is changed to the torque required by the driver. The control of the transmission according to any one of claims 1 to 4, further comprising a drive source control means for controlling the rotation speed of the turbine and the rotation speed of the input shaft of the transmission mechanism. apparatus.

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