JP5863379B2 - Dual clutch type automatic transmission and its shift control method - Google Patents

Description

  The present invention relates to a dual clutch type automatic transmission having a dual clutch capable of transmitting the rotational driving force of a prime mover to each of two input shafts, and a transmission control method therefor.

  2. Description of the Related Art In recent years, attention has been focused on a dual clutch type automatic transmission that can eliminate a torque interruption during a shift change as shown in Patent Document 1. Such a dual clutch type automatic transmission supports two input shafts that are concentrically provided and fixed to even-numbered gears and odd-numbered gears, respectively, and even-numbered and odd-numbered driven gears that are arranged in parallel to the input shafts. And a second countershaft that supports the remaining driven gear among the even-numbered and odd-numbered driven gears. Two clutches for connecting and disconnecting torque transmission are provided between the engine and the two input shafts.

  With such a configuration, the dual clutch type automatic transmission has a clutch connected to one input shaft in an engaged state, and engine torque is transmitted from one input shaft to the other via a predetermined gear stage (actual gear stage). The vehicle is driven by rotating the countershaft. At this time, on the other input shaft in which the clutch is disengaged, the control device predicts (requests) a predetermined gear stage to be shifted next from the traveling state of the vehicle, the operation state of the accelerator, etc. The predicted gear stage (requested gear stage) is established and is on standby. For example, when the driver wants to accelerate and depresses the accelerator, and the vehicle speed reaches the shift point, the engagement of the clutch of one connected input shaft is disengaged and released. At the same time, the clutch of the other input shaft that was in the disconnected state is engaged, and eventually the engine torque is completely transmitted to the other input shaft through the gear stage (requested gear stage) that has been on standby. The vehicle runs by driving the wheels. As a result, the speed change operation is completed in a short time, and the torque is not easily lost during the speed change.

JP 2010-196745 A

  In the prior art described in Patent Document 1, for example, when the downshift is being performed and the required gear is a gear that is two speeds lower than the actual gear, the input corresponding to the actual gear and the required gear The axis is the same input axis. When shifting between the same input shafts in this way, after the actual gear stage is released, a timing at which torque cannot be transmitted to the wheels occurs during the shift gear stage switching control for establishing the required gear stage. Therefore, in order to transmit torque to the wheels without interruption, the relay gear stage (established at the other input shaft) is the gear stage between the actual gear stage and the required gear stage before the engagement control at the required gear stage. There is a control method in which a clutch corresponding to the input shaft for which the above is established is engaged and controlled in a so-called half-clutch state. However, if the torque transmitted to the wheels when the relay gear stage is engaged and controlled in a half-clutch state at this time is small, there is a risk that the driver may feel a feeling of rattling due to a decrease in torque.

  The present invention has been made in view of the above-described problem, and is a shift from the actual gear stage to the requested gear stage when the downshift is being performed and the requested gear stage is a gear stage that is two speeds lower than the actual gear stage. An object of the present invention is to provide a dual clutch type automatic transmission capable of satisfying the acceleration feeling desired by the driver and a method for controlling the shift.

In order to solve the above problems, the invention of a dual clutch automatic transmission according to claim 1 is characterized in that the first input shaft and the second input shaft arranged concentrically, and the rotational driving force of a motor of a vehicle are the first. A dual clutch having a first clutch for transmitting to one input shaft and a second clutch for transmitting the rotational driving force to the second input shaft, and an odd number by shifting the rotational driving force transmitted to the first input shaft A first shift mechanism that establishes a shift speed; a second shift mechanism that shifts the rotational driving force transmitted to the second input shaft to establish an even speed shift stage; and an accelerator depression that detects an accelerator depression amount of the accelerator When the shift detection command is sent to the amount detection unit, an actual gear stage that is disconnected from the prime mover of the first input shaft and the second input shaft of the first clutch and the second clutch is formed. Required gear clutch corresponding to the input shaft, which is connected to disconnection control for dissecting by controlling the clutch torque lines as Utotomoni, the prime mover of said first input shaft and the second input shaft to the clutch corresponding to the input shaft stage is established, and a shift control device for performing engagement control to engage by controlling the clutch torque, the transmission control device, the required gear downshift by the shift command the required gear stage when the stage is transmitted is, the current engaged with is to have the input shaft corresponding to the clutch actually satisfied to have the actual gear stage and requests determines matching gear determining unit, When the required gear stage determination unit determines that the required gear stage does not match the actual gear stage, the detected accelerator depression amount and the speed ratio of the required gear stage are determined. Thereby calculating the required gear stage prediction vehicle acceleration of the vehicle in the required gear speed after shifting by Zui is the gears in between said detected amount of accelerator pedal depression, the required gear stage as the actual gear stage It is calculated based on the gear ratio of the relay gear and the output driving force of the prime mover, which is the clutch torque when the relay gear is subjected to the engagement control, and the target speed change speed required for the prime mover. based on the size of goals clutch torque, and the relay gear is predicted vehicle acceleration calculator for calculating a relay gear prediction vehicle acceleration of the vehicle when being the engagement control by the target clutch torque, the When the calculated relay gear stage predicted vehicle acceleration has a ratio equal to or greater than a certain ratio to the calculated required gear stage predicted vehicle acceleration , the actual gear stage And determining that the relay gear stage is to be shifted in the shift to the required gear stage, and when the relay gear stage predicted vehicle acceleration does not have a ratio greater than or equal to the predetermined gear stage predicted vehicle acceleration, A shift method determination unit that determines that the relay gear is not passed in shifting from the actual gear to the required gear .

Invention of the dual clutch type automatic transmission according to claim 2, Oite to claim 1, wherein the transmission control device, when the required gear stage by the required gear speed determining portion does not coincide with the actual gear stage A dual clutch automatic transmission including an input shaft coaxial determination unit that determines whether or not the input shafts corresponding to the required gear stage and the actual gear stage are the same when determined.

According to a third aspect of the invention, there is provided a shift control method for a dual clutch automatic transmission, wherein the first input shaft and the second input shaft that are concentrically arranged, and the rotational driving force of a prime mover of a vehicle are transmitted to the first input shaft. A first clutch that rotates and a dual clutch that has a second clutch that transmits the rotational driving force to the second input shaft, and shifts the rotational driving force transmitted to the first input shaft to establish an odd gear. A first shift mechanism, a second shift mechanism that shifts the rotational driving force transmitted to the second input shaft to establish an even-numbered gear stage, an accelerator depression amount detection unit that detects an accelerator depression amount of an accelerator, When a gear shift command is sent, the first clutch and the second clutch of the first input shaft and the second input shaft that are separated from the prime mover are set to the input shaft that establishes the actual gear stage. The clutch response, row a disconnection control for dissecting by controlling the clutch torque Utotomoni, required gear stage in which the connected to a prime mover of said first input shaft and the second input shaft is established the clutch corresponding to the input shaft, a shift control method of the dual clutch type automatic transmission and a shift control device for performing engagement control to engage by controlling the clutch torque, the transmission control method, whether the required gear stage when the required gear stage downshift in the gear shift command is transmitted is consistent with the actual gear stage that is actually established in the input shaft which corresponds to the clutch that is currently engaged Detected when it is determined that the required gear stage does not match the actual gear stage by the required gear stage determining step and the required gear stage determining step. The accelerator depression amount and the request with gear position based on the speed ratio for calculating the required gear stage prediction vehicle acceleration of the vehicle in the required gear stage after shifting, said detected accelerator depression amount, and the required gear stage Requested from the prime mover and the output driving force of the prime mover that is the clutch torque when the relay gear stage is engaged and controlled. based on the size of goals clutch torque calculated based on the target speed shift level to be the relay gear prediction of the vehicle in a case where the relay gear is the engagement control by the target clutch torque A predicted vehicle acceleration calculating step for calculating vehicle acceleration; and the calculated relay gear predicted vehicle addition to the calculated required gear predicted vehicle acceleration. When the speed has a ratio equal to or greater than a certain value, it is determined that the relay gear stage is interposed in the shift from the actual gear stage to the required gear stage, and the relay gear stage with respect to the required gear stage predicted vehicle acceleration is determined. A shift method determining step for determining that the relay gear stage is not passed in the shift from the actual gear stage to the required gear stage when the predicted vehicle acceleration does not have a ratio greater than or equal to the predetermined level .

According to the invention of the dual clutch type automatic transmission according to the first aspect, when the shift command is transmitted by the downshift required gear stage, and it is determined that the actual gear stage and the required gear stage do not match, the predicted vehicle The acceleration calculation unit calculates a required gear stage predicted vehicle acceleration when the required gear stage is established. Further, when there is a relay gear stage between the actual gear stage and the required gear stage, a relay gear stage predicted vehicle acceleration when the relay gear stage is established is calculated.
The required gear stage predicted vehicle acceleration is calculated based on the detected accelerator depression amount and the required gear stage gear ratio. Further, the relay gear stage predicted vehicle acceleration is calculated based on the detected accelerator depression amount, the gear ratio of the relay gear stage, and the magnitude of the target clutch torque at which the relay gear stage is controlled to be engaged. Then, according to the relationship between the calculated required gear stage predicted vehicle acceleration and the relay gear stage predicted vehicle acceleration, the speed change method determination unit determines whether or not the shift from the actual gear stage to the required gear stage is performed via the relay gear stage. judge. As described above, since the predicted vehicle acceleration at the relay gear stage is actually calculated to determine the influence of the relay gear stage, it is possible to eliminate the case where a feeling of torque slack occurs with high accuracy.

According to the invention of a dual clutch type automatic transmission according to claim 2, when Oite to claim 1, the shift control device, the required gear stage is determined not to match the actual gear stage, required gear An input shaft coaxial determination unit is provided for determining whether the input shafts corresponding to the gear and the actual gear are the same. If the input shafts corresponding to the requested gear stage and the actual gear stage are the same, it can be seen that the requested gear stage and the actual gear stage are even-numbered gear stages or odd-numbered gear stages, and the gear stages are separated by two stages. If they are not the same, it can be seen that the gear stage difference is one stage. As described above, after the input shaft coaxial determination unit determines that the required gear stage and the actual gear stage are separated by two stages and has a relay gear stage, the predicted vehicle acceleration calculation unit calculates the required gear stage predicted vehicle acceleration. Further, since the predicted vehicle speed of the relay gear stage is calculated, there is no waste and it is efficient.

According to the invention of the speed change control method according to claim 3, having the same effect as claim 1.

1 is a block diagram showing a partial configuration of a vehicle to which a dual clutch type automatic transmission according to the present invention can be applied. It is a skeleton figure which shows the structure of the transmission part of a dual clutch type automatic transmission. It is a figure which shows the drive mechanism of a fork. It is a graph which shows the relationship of clutch actuator operation amount-clutch torque. It is a figure explaining the shift line of an upshift and a downshift. It is a figure explaining the relationship between the vehicle speed and vehicle acceleration in each transmission gear stage. It is a figure explaining each part state at the time of carrying out gear shift control via a relay gear stage. It is a figure explaining each part state at the time of carrying out shift control without going through a relay gear stage. It is the flowchart which showed the control method of the transmission control apparatus which concerns on 1st Embodiment.

  Hereinafter, a first embodiment of a dual clutch automatic transmission embodying the present invention will be described with reference to FIGS. FIG. 1 is a block diagram showing a configuration of a part of a vehicle to which a dual clutch type automatic transmission 1 according to the present invention can be applied. The vehicle shown in FIG. 1 is an FF (front engine front drive) type vehicle, which is an example of a prime mover, which is an engine 4 driven by combustion of gasoline, the dual clutch automatic transmission 1 according to the present invention, and a differential device 14. (Differential), drive shafts 15a and 15b, drive wheels 16a and 16b (front wheels), and driven wheels (rear wheels) (not shown). 1 is a top view of the vehicle, and the upper side of FIG. 1 corresponds to the front of the vehicle.

  As shown in FIG. 2, the dual clutch automatic transmission 1 includes a transmission case 11 in which a plurality of gear stages are formed and stored, and a clutch housing 12 that stores a dual clutch 40 (corresponding to the dual clutch of the present invention). Have. A case 10 is formed by the transmission case 11 and the clutch housing 12.

  Further, the dual clutch automatic transmission 1 switches a plurality of gear stages accommodated in the transmission case 11 (shift shift) and a first clutch disk 41 (which constitutes the first clutch of the present invention) of the dual clutch 40. ) And the second clutch disc 42 (which constitutes the second clutch of the present invention). The speed change control device is configured by an ECU 2 (Engine Control Unit) and a TCU 3 (Transmission Control Unit).

  As shown in FIG. 1, the ECU 2 includes an output shaft speed sensor 4a of the engine 4 provided in the vicinity of the drive shaft 4b of the engine 4, a motor for opening and closing a throttle valve of the throttle body of the engine 4, and a throttle valve of the throttle body. A throttle opening sensor for detecting the opening, an injector for performing fuel injection (both not shown), an accelerator opening sensor 27 provided on the accelerator pedal P, and the like are connected. As a result, data is exchanged with each device or a control command is issued to each device. For example, the motor is driven to control the throttle opening of the throttle body based on the above information including data obtained from the TCU 3, or the fuel injection amount of the injector is controlled. The engine speed Ne which is the engine speed is controlled.

  As shown in FIG. 1, the TCU 3 outputs the DC electric motors 19a and 19b and the DC electric motors 19a and 19b included in the first and second clutch actuators 17 and 18 that perform switching control of the dual clutch 40 described later. Stroke sensors 17a and 18a for detecting the stroke to be performed, vehicle speed sensors 23a and 23b for detecting the vehicle speed, and first and second input shaft rotational speed sensors 24a and 24b are connected. The TCU 3 is connected to each motor 131 of a fork drive mechanism 130 that operates first to fourth shift clutches 101 to 104, which will be described later, and shift stroke sensors 136 to 139 for detecting a stroke (see FIG. 3). ). As a result, the TCU 3 exchanges data with each device or issues a control command to each device. The TCU 3 is connected to the ECU 2 and appropriately controls the shift of the dual clutch automatic transmission 1 while exchanging information with the ECU 2 through CAN communication.

  As shown in FIG. 2, the dual clutch automatic transmission 1 is a seven-speed forward dual clutch automatic transmission, and in the axial direction within the case 10, a first input shaft 21, a second input shaft 22, A first countershaft 31 and a second countershaft 32 are provided. The case 10 also includes a dual clutch 40, drive gears 51 to 57 for each gear stage, final reduction drive gears 58 and 68, driven gears 61 to 67 for each gear stage, a reverse gear 70, and a ring gear 80. . Hereinafter, the same axial direction as the first input shaft 21, the second input shaft 22, the first auxiliary shaft 31, and the second auxiliary shaft 32 is referred to as an input axis direction.

  The first input shaft 21 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing. A portion for supporting the bearing and a plurality of external tooth splines are formed on the outer peripheral surface of the first input shaft 21. The first input shaft 21 is directly formed with a plurality of odd speed drive gears, a first speed drive gear 51 and a third speed drive gear 53. Further, a plurality of fifth-speed drive gears 55 and seventh-speed drive gears 57 that are odd-numbered stage drive gears are press-fitted and fixed to external splines formed on the outer peripheral surface of the first input shaft 21 by spline fitting. Further, a connecting portion (spline) that is spline-engaged with the inner diameter portion of the first clutch disc 41 is formed on the outer peripheral surface of the end portion of the first input shaft 21. The inner diameter portion of the first clutch disk 41 is engaged with the connecting portion (spline) and can move forward and backward in the input shaft direction on the first input shaft 21.

  The second input shaft 22 is formed in a hollow shaft shape, and is rotatably supported on the outer periphery of a part of the first input shaft 21 via a plurality of bearings. The transmission case 11 and the clutch housing are supported by the bearings. 12 is supported rotatably. That is, the second input shaft 22 is disposed so as to be rotatable relative to the first input shaft 21 concentrically. Similarly to the first input shaft 21, a portion for supporting the bearing and a plurality of external gears are formed on the outer peripheral surface of the second input shaft 22. The second input shaft 22 is formed with a plurality of even speed drive gears, a second speed drive gear 52, a fourth speed drive gear 54, and a sixth speed drive gear 56. Further, a connecting portion (spline) that is spline-engaged with the inner diameter portion of the second clutch disk 42 is formed on the outer peripheral surface of the end portion of the second input shaft 22. The inner diameter portion of the second clutch disk 42 is engaged with the connecting portion (spline) and can move forward and backward in the input shaft direction on the second input shaft 22.

  The first countershaft 31 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in parallel to the first input shaft 21 in the transmission case 11. A final reduction drive gear 58 is formed on the outer peripheral surface of the first countershaft 31, and a portion for supporting the bearing and a plurality of external splines are formed. Further, the first countershaft 31 is formed with a support portion that supports the first-speed driven gear 61, the third-speed driven gear 63, the fourth-speed driven gear 64, and the reverse gear 70 so as to be freely rotatable.

  The external splines of the first countershaft 31 include a first shift clutch 101 (corresponding to the first shift mechanism of the present invention) and a third shift clutch 103 (corresponding to the second shift mechanism of the present invention) described later. Each clutch hub 201 is press-fitted by spline fitting. The final reduction drive gear 58 meshes with the ring gear 80 of the differential 14 (differential) shown in FIG.

  A first-speed driven gear 61 that is supported by the support portion of the first countershaft 31 so as to be free-wheeling meshes with a first-speed drive gear 51 formed on the first input shaft 21, and a first-speed gear stage (an odd-numbered speed change according to the present invention). Corresponds to the step). When the first gear driven gear 61 is selected by the TCU 3 as the required gear stage Gd, the sleeve 202 of the first shift clutch 101 moves to the first gear driven gear 61 side, and the first gear driven gear 61, the first countershaft 31, Is connected so that relative rotation is impossible. As a result, the first-speed driven gear 61 and the first countershaft 31 are integrally rotated (this state is referred to as a state in which the first-speed gear stage is established. The same applies to the above). At this time, the operating state of the first shift clutch 101 is monitored by the shift stroke sensor 136 for the first shift clutch 101 and the current state of the first shift clutch 101 is grasped by the TCU 3. Thereafter, the same applies to the second shift clutch 102 to the fourth shift clutch 104.

  A third-speed driven gear 63 that is supported by the support portion of the first countershaft 31 so as to be free-wheeling meshes with a third-speed drive gear 53 formed on the first input shaft 21, and a third-speed gear stage (an odd number of the present invention). Corresponding to the gear position). When the third speed driven gear 63 is selected by the TCU 3, the sleeve 202 of the first shift clutch 101 moves to the third speed driven gear 63 side so that the third speed driven gear 63 and the first countershaft 31 cannot be rotated relative to each other. Connecting. As a result, the third speed driven gear 63 and the first countershaft 31 are rotated integrally (a state where the third speed gear stage is established).

  A four-speed driven gear 64 that is supported by the support portion of the first countershaft 31 so as to be free-wheeling meshes with a four-speed drive gear 54 formed on the second input shaft 22, and a four-speed gear stage (even number of the present invention). Corresponding to the gear position). When the 4-speed driven gear 64 is selected by the TCU 3, the sleeve 202 of the third shift clutch 103 moves to the 4-speed driven gear 64 side so that the 4-speed driven gear 64 and the first countershaft 31 cannot be rotated relative to each other. Connecting. As a result, the fourth speed driven gear 64 and the first countershaft 31 rotate integrally (fourth speed gear stage established state).

  Further, when the reverse gear 70 supported by the TCU 3 so as to be freely rotatable on the support portion of the first countershaft 31 is selected, the sleeve 202 of the third shift clutch 103 moves to the reverse gear 70 side, and the reverse gear 70 and The first counter shaft 31 is connected so as not to be relatively rotatable. As a result, the reverse gear 70 and the first countershaft 31 rotate integrally (reverse gear stage establishment state). The reverse gear 70 always meshes with a small-diameter gear 62a formed integrally with a second-speed driven gear 62 that is supported by the second countershaft 32 so as to be free to rotate.

  The second countershaft 32 is rotatably supported with respect to the transmission case 11 and the clutch housing 12 by a bearing, and is disposed in parallel to the first input shaft 21 in the transmission case 11. Further, on the outer peripheral surface of the second countershaft 32, as with the first countershaft 31, a final reduction drive gear 68 is formed, and a portion for supporting the bearing and a plurality of external splines are formed. The external spline of the second countershaft 32 includes a second shift clutch 102 (corresponding to the second shift mechanism of the present invention) and a fourth shift clutch 104 (corresponding to the first shift mechanism of the present invention). The clutch hub 201 is press-fitted by spline fitting. The final reduction drive gear 68 meshes with the ring gear 80 of the differential device 14. The ring gear 80 is meshed with the final reduction drive gear 58 and the final reduction drive gear 68, so that the ring gear 80 is always rotationally connected to the first auxiliary shaft 31 and the second auxiliary shaft 32. The ring gear 80 is rotationally connected to the drive shafts 15 a and 15 b and the drive wheels 16 a and 16 b via an output shaft (not shown) supported by the case 10 and the differential device 14. Further, the second countershaft 32 is formed with a support portion that supports the second speed driven gear 62, the fifth speed driven gear 65, the sixth speed driven gear 66, and the seventh speed driven gear 67 so as to be freely rotatable. Yes.

  A second-speed driven gear 62 supported rotatably on the support portion of the second countershaft 32 meshes with a second-speed drive gear 52 formed on the second input shaft 22, and a second-speed gear stage (the even speed change of the present invention). Corresponds to the step). When the second speed driven gear 62 is selected by the TCU 3, the sleeve 202 of the second shift clutch 102 moves to the second speed driven gear 62 side so that the second speed driven gear 62 and the second countershaft 32 cannot be rotated relative to each other. Connecting. As a result, the second speed driven gear 62 and the second countershaft 32 rotate integrally (second speed gear stage established state).

  Further, the 5-speed driven gear 65 supported by the support portion of the second countershaft 32 so as to be free-wheeling meshes with the 5-speed drive gear 55 formed on the first input shaft 21, and the 5-speed gear stage (the present invention). Corresponding to an odd number of gears). When the fifth speed driven gear 65 is selected by the TCU 3, the sleeve 202 of the fourth shift clutch 104 moves to the fifth speed driven gear 65 side so that the fifth speed driven gear 65 and the second countershaft 32 cannot be rotated relative to each other. Connecting. As a result, the fifth-speed driven gear 65 and the second countershaft 32 rotate integrally (a fifth-speed gear stage is established).

  Further, the 6-speed driven gear 66 supported so as to be free to rotate by the support portion of the second countershaft 32 meshes with the 6-speed drive gear 56 formed on the second input shaft 22, and the 6-speed gear stage (the present invention). Corresponding to an even number of gears). When the 6-speed driven gear 66 is selected by the TCU 3, the sleeve 202 of the second shift clutch 102 moves to the 6-speed driven gear 66 side so that the 6-speed driven gear 66 and the second countershaft 32 cannot be rotated relative to each other. Connecting. As a result, the 6-speed driven gear 66 and the second countershaft 32 rotate together (a 6-speed gear stage is established).

  Further, the seventh speed driven gear 67 supported by the support portion of the second countershaft 32 so as to be free-wheeling meshes with the seventh speed drive gear 57 formed on the first input shaft 21, and the seventh speed gear stage (the present invention). Corresponding to an odd number of gears). When the 7-speed driven gear 67 is selected by the TCU 3, the sleeve 202 of the fourth shift clutch 104 moves to the 7-speed driven gear 67 side so that the 7-speed driven gear 67 and the second countershaft 32 cannot be rotated relative to each other. Connecting. As a result, the seventh-speed driven gear 67 and the second countershaft 32 rotate integrally (a seventh-speed gear stage is established).

  Next, the dual clutch 40 will be described with reference to FIGS. 1 and FIG. 2 may look different in configuration, the dual clutch 40 in FIG. 2 is a simpler illustration than the dual clutch 40 in FIG. 1. The dual clutch 40 in FIG. 2 is the same.

  The dual clutch 40 is provided concentrically with the first input shaft 21 and the second input shaft 22. The dual clutch 40 is accommodated in the clutch housing 12 on the right side of FIG. 2 and, as shown in FIGS. 1 and 2, the first and second clutch disks 41 and 42, the center plate 43, and the first and second pressure plates 44. , 45 and first and second diaphragm springs 46, 47 (see FIG. 1). At this time, the first clutch disk 41, the center plate 43, the first pressure plate 44, and the first diaphragm spring 46 constitute the first clutch of the present invention. The second clutch disk 42, the center plate 43, the second pressure plate 45, and the second diaphragm spring 47 constitute the second clutch of the present invention.

  The first clutch disc 41 transmits the rotational drive torque Ter of the engine 4 (corresponding to the rotational drive force of the present invention) to the first input shaft 21, and the second clutch disc 42 receives the rotational drive torque Ter of the engine 4 as two inputs. It is transmitted to the shaft 22. The first clutch disc 41 is spline-engaged to the connecting portion of the first input shaft 21 so as to be movable in the input shaft direction, and the second clutch disc 42 is movable to the connecting portion of the second input shaft 22 in the input shaft direction. The spline is engaged.

  As shown in FIGS. 1 and 2, the center plate 43 has a surface between the first clutch disk 41 and the second clutch disk 42 facing the surfaces of the first and second clutch disks 41 and 42 in parallel. Has been placed. The center plate 43 is provided between the outer peripheral surface of the second input shaft 22 so as to be rotatable relative to the second input shaft 22 via a ball bearing, and is connected to the drive shaft 4b of the engine 4 and integrally rotates.

  As shown in FIGS. 1 and 2, the first and second pressure plates 44 and 45 sandwich the first and second clutch disks 41 and 42 between the first and second clutch disks 41 and 42, respectively. The discs 41 and 42 are arranged so as to be crimped.

  The first and second diaphragm springs 46 and 47 shown in FIG. 1 are formed in a disc shape. The first diaphragm spring 46 is disposed on the opposite side of the first pressure plate 44 in the input shaft direction around the center plate 43. The outer diameter portion of the first diaphragm spring 46 and the first pressure plate 44 are connected by a cylindrical connecting portion 44a. The first diaphragm spring 46 is supported by the tip of the arm 43 a that extends from the center plate 43. In this state, the first pressure plate 44 is separated from the first clutch disc 41 when the connecting portion 44a is biased toward the engine 4 by the spring force that biases the outer diameter portion of the first diaphragm spring 46 toward the engine 4. .

  When the inner diameter portion of the first diaphragm spring 46 is pressed toward the engine 4 side, the spring force of the outer diameter portion of the first diaphragm spring 46 toward the engine 4 is attenuated. At the same time, the outer diameter portion of the first diaphragm spring 46 moves in the opposite direction to the engine 4 with the tip of the arm portion 43 a extending from the center plate 43 as a fulcrum. As a result, the first pressure plate 44 moves in the direction of the first clutch disk 41 and eventually the first clutch disk 41 is sandwiched and pressed against the center plate 43. Then, it is completely engaged and the rotational drive torque Ter of the engine 4 is transmitted to the first input shaft 21. In the above description, the pressing force for pressing the inner diameter portion of the first diaphragm spring 46 is controlled by the actuator operation amount L1 when the inner diameter portion is pressed, and details thereof will be described later.

  The second diaphragm spring 47 is disposed on the transmission side of the second pressure plate 45 and on the engine 4 side of the arm portion 43 a of the center plate 43, and faces the second pressure plate 45. The outer diameter portion of the second diaphragm spring 47 is arranged so that the spring force of the outer diameter portion urges the arm portion 43a extending from the center plate 43 toward the transmission side. As a result, the second pressure plate 45 is not pressed against the second clutch disk 42 in a normal state. When the inner diameter portion of the second diaphragm spring 47 is pressed toward the engine 4 side, the vicinity of the pressing portion moves in the direction of the engine 4 with the outer diameter portion of the second diaphragm spring 47 contacting the arm portion 43a as a fulcrum. As a result, the second pressure plate 45 is pushed by the diaphragm spring 47 and moves in the direction of the second clutch disc 42, and the second clutch disc 42 is sandwiched and pressed against the center plate 43. Then, it is completely engaged and the rotational drive torque Ter of the engine 4 is transmitted to the second input shaft 22. Similar to the first diaphragm spring 46, the pressing force for pressing the inner diameter portion of the second diaphragm spring 47 is controlled by the actuator operation amount L2 when the inner diameter portion is pressed.

  The pressing of the inner diameter portions of the first diaphragm spring 46 and the second diaphragm spring 47 described above is controlled by the first and second clutch actuators 17 and 18 (corresponding to the clutch actuator of the present invention) shown in FIG. The first and second clutch actuators 17 and 18 are respectively DC motors 19a and 19b, rods 25a and 25b that linearly move by a ball screw structure by the operation of the DC motors 19a and 19b, and straight lines of the rods 25a and 25b. Transmitting portions 26a, 26b that transmit the movement to the inner diameter portions of the first and second diaphragm springs 46, 47 by a link mechanism, and stroke sensors 17a, which detect actuator operating amounts L1, L2 of the linear motion of the rods 25a, 25b, 18a. And the information regarding the actuator operation amounts L1 and L2 of the rods 25a and 25b detected by the stroke sensors 17a and 18a is transmitted to the TCU3.

  Since the dual clutch 40 is configured in this way, when a shift command is sent from the TCU 3 to the first or second clutch actuators 17 and 18, the TCU 3 activates the first or second clutch actuators 17 and 18 according to a predetermined actuator operation. The clutch torque Tc transmitted from the engine 4 to the input shaft is controlled by operating toward the transmission side by the amounts L1 and L2. As a result, the TCU 3 disconnects the clutch corresponding to the input shaft disconnected from the engine 4 of the first input shaft 21 and the second input shaft 22 of the first clutch disc 41 and the second clutch disc 42. Take control.

  At the same time, the TCU 3 is connected to the engine 4 of the first input shaft 21 and the second input shaft 22 of the first clutch disc 41 constituting the first clutch and the second clutch disc 42 constituting the second clutch. The clutch disk of the clutch corresponding to the input shaft has a clutch torque Tc based on the output drive torque Te of the engine 4 (corresponding to the output drive force of the present invention) and the target rotational speed variation ΔNet required for the engine 4. The target clutch torque Tca calculated in this way is controlled (details will be described later). Then, when the rotational speed Ne of the engine 4 synchronizes with the rotational speed Ni1 or Ni2 of the input shaft to be connected, engagement control is performed. Specifically, the DC electric motor 19a or 19b is operated, and the operation of the rod 25a or 25b is controlled to press the inner diameter portion of the first or second diaphragm springs 46 and 47 toward the engine 4 side.

  Next, the 1st-4th shift clutch 101-104 is demonstrated based on FIG. 2, FIG. Each of the forks 72a, 72b, 72c, 72d shown in FIGS. 2 and 3 engages with the outer peripheral portion of the sleeve 202 included in the first to fourth shift clutches 101 to 104 and slides the sleeve 202 in the input shaft direction. It is. Each fork 72a-72d is driven by the respective fork drive mechanism 130.

  In the present embodiment, four fork drive mechanisms 130 are provided to drive the first to fourth shift clutches 101 to 104, respectively. As shown in FIG. 3, each fork drive mechanism 130 includes a motor 131 having a worm gear 132 formed on a rotating shaft, a worm wheel 133 meshing with the worm gear 132, and a pinion gear 134 formed integrally with the worm wheel 133. , A rack shaft 135 that meshes with the pinion gear 134 is provided. The rack shaft 135 is integrally provided with the forks 72a to 72d. That is, by rotating the motor 131 of each fork drive mechanism 130, the forks 72 a to 72 d connected to the motor 131 slide in the axial direction of the first countershaft 31 or the second countershaft 32.

  Further, as shown in FIG. 3, shift stroke sensors 136 to 139 for detecting a stroke amount by which the forks 72 a to 72 d slide and move in the axial direction are provided in the vicinity of the rotation shaft of the pinion gear 134. The shift stroke sensors 136 to 139 are connected to the TCU 3, and the rotation speed of the worm wheel 133 is converted into a stroke amount by the calculation unit of the TCU 3. The shift stroke sensors 136 to 139 may be provided in the vicinity of the rotation axis of the motor 131, respectively.

  The first shift clutch 101 is disposed between the first speed driven gear 61 and the third speed driven gear 63 in the axial direction of the first countershaft 31. The second shift clutch 102 is disposed between the second speed driven gear 62 and the sixth speed driven gear 66 in the axial direction of the second countershaft 32. The third shift clutch 103 is disposed between the fourth speed driven gear 64 and the reverse gear 70 in the axial direction of the first countershaft 31. Further, the fourth shift clutch 104 is disposed between the fifth speed driven gear 65 and the seventh speed driven gear 67 in the axial direction of the second countershaft 32.

  As shown in FIG. 2, the first shift clutch 101 includes a clutch hub 201, a first speed engagement member 205, a third speed engagement member 205, a synchronizer ring 203, and a sleeve 202. The clutch hub 201 is splined to the first countershaft 31. The first-speed engagement member 205 is press-fitted and fixed to the first-speed driven gear 61, and the third-speed engagement member 205 is press-fitted and fixed to the third-speed driven gear 63. The synchronizer ring 203 is interposed between the clutch hub 201 and the left and right engaging members 205, 205, respectively. The sleeve 202 is splined to the outer periphery of the clutch hub 201 so as to be movable in the axial direction. The first shift clutch 101 is a known synchromesh mechanism that removably connects the driven gears 61 and 63 to the first input shaft 21.

  The sleeve 202 of the first shift clutch 101 is not engaged with any of the engagement members 205 and 205 in the neutral position. However, the rack shaft 135 is driven in the input shaft direction by the operation of the fork drive mechanism 130, and the sleeve 202 is moved to the first speed driven gear 61 side by the fork 72a fixed to the rack shaft 135 and engaged with the annular groove on the outer periphery of the sleeve 202. When shifted, the internal teeth (not shown) of the sleeve 202 are spline-engaged with the synchronizer ring 203 on the first-speed driven gear 61 side. Then, the rotation of the first countershaft 31 and the first speed driven gear 61 is synchronized while pressing the synchronizer ring 203 against the first speed driven gear 61. Next, the inner teeth of the sleeve 202 are engaged with the external splines on the outer periphery of the first-speed engagement member 205, and the first countershaft 31 and the first-speed driven gear 61 are integrally connected to establish the first-speed gear stage. . Further, if the fork 72a causes the fork 72a to shift the sleeve 202 toward the third speed driven gear 63, the first countershaft 31 and the third speed driven gear 63 are similarly synchronized with each other after the rotation of the first countershaft 31 and the third speed driven gear 63 is synchronized. To establish a third gear.

  The second to fourth shift clutches 102 to 104 are substantially the same in structure as the first shift clutch 101 and only have different attachment positions. The second shift clutch 102 selectively couples the second speed driven gear 62 and the sixth speed driven gear 66 to the second countershaft 32 to disable relative rotation, and establishes the second speed gear stage and the sixth speed gear stage. In addition, the third shift clutch 103 selectively connects the fourth speed driven gear 64 and the reverse gear 70 to the first countershaft 31 to disable relative rotation, and establishes the fourth speed gear stage and the reverse gear stage. Further, the fourth shift clutch 104 selectively connects the fifth speed driven gear 65 and the seventh speed driven gear 67 to the second countershaft 32 to make the relative rotation impossible, and establishes the fifth speed gear stage and the seventh speed gear stage.

As shown in FIG. 1, the ECU 2 includes an accelerator depression amount detection unit 2a and a prime mover rotation speed detection unit 2b.
The accelerator depression amount detection unit 2a includes an accelerator opening sensor 27 and detects the depression of the accelerator depressed by the driver and the accelerator depression amount Lac. Specifically, the accelerator opening acquired from the accelerator opening sensor 27 is detected as the depression amount.
The prime mover rotational speed detector 2b includes an output shaft rotational speed sensor 4a provided in the vicinity of the drive shaft 4b of the engine 4, and detects the engine rotational speed Ne by the output shaft rotational speed sensor 4a.

  The TCU 3 has a shift clutch control unit (not shown) that controls the fork drive mechanism 130 that operates the first to fourth shift clutches 101 to 104 as described above. Further, the TCU 3 has a shift control unit 3a. When a shift command to the required gear stage Gd is sent, the TCU 3 is engaged between the first clutch disk 41 and the second clutch disk 42 by the shift control unit 3a. One clutch disk in which the actual gear stage Gp is established is disengaged and the other clutch disk in which the required gear stage Gd is established is engaged. Here, the required gear stage Gd refers to the gear position to be selected next to the current gear stage Gp requested by the TCU 3 based on the accelerator operation state of the driver, the traveling state of the vehicle, the shift line, and the like. Actually, the calculation of the required gear stage Gd is performed based on a shift line prepared in advance and stored in the ROM of the TCU 3.

  For example, the shift lines shown in FIG. 5 are representatively, for example, a shift line A from the 4th speed stage to the 5th speed stage on the upshift side, a shift line B from the 5th speed stage to the 6th speed stage, and 6 on the downshift side. The shift line D from the fifth gear to the fifth gear and the shift line C from the fifth gear to the fourth gear are shown. The shift line is map data used at the time of shifting of the vehicle. The gear selection parameter (vehicle speed V and accelerator pedal opening in the present embodiment) selected in advance is set for each axis, and from one gear stage to another gear stage. This is a reference line for determining whether or not shifting is required.

  As shown in FIG. 5, the dual clutch automatic transmission 1 has pre-shift lines a and b indicated by broken lines slightly before the up-shift side shift lines A and B. The pre-shift lines a and b are fork driven when the relationship between the predetermined accelerator opening (accelerator depression amount Lac) and the vehicle speed V exceeds the pre-shift lines a and b while the vehicle speed V is moving toward the high gear stage. This is a shift line for starting a shift to a gear stage (required gear stage Gd) corresponding to each pre-shift line that has been exceeded by the mechanism 130. Similarly, pre-shift lines c and d indicated by broken lines are provided slightly before the shift lines C and D on the downshift side during deceleration. As a result, when the accelerator pedal P is turned off or loosened, the vehicle speed V decelerates, or as shown by the one-dot chain line in FIG. 5, the relationship between the accelerator opening and the vehicle speed V indicates the pre-shift line c. , D is shifted toward the low gear position side, the fork drive mechanism 130 starts shifting to the gear stage (required gear stage Gd) corresponding to the pre-shift lines c, d.

  When an up-shift command for shifting up from a fourth gear to a gear with a small gear ratio, such as a fifth gear, is sent, the following gear change control is performed. The shift control unit 3a (which constitutes the shift control device according to the present invention) first operates the second clutch actuator 18 and is connected to the second input shaft 22 to which the fourth speed drive gear 64 is fixed. Separation control is performed to separate 42 while controlling 42 with a predetermined clutch torque Tc.

  At the same time, the shift control unit 3a operates the first clutch actuator 17 to set the first clutch disk 41 connected to the first input shaft 21 to which the established fifth speed drive gear 55 is fixed. Engagement control is performed such that the engine speed Ne and the first input shaft speed Ni1 are connected in synchronization with each other, controlled by Tca. At this time, the engine rotational speed Ne is detected by the prime mover rotational speed detector 2b, and the first input shaft rotational speed Ni1 is detected by the input shaft rotational speed sensor 24a. Then, when the engine speed Ne is synchronized with the first input shaft speed Ni1, the shift control unit 3a operates the clutch actuator operating amount L1 of the first clutch actuator 17 to the maximum amount and completely connects the first clutch disk 41. .

  Here, in the upshift as described above, assuming that the vehicle speed V before and after the shift is constant, the gear ratio of the shift gear stage is small. For this reason, the first input shaft rotational speed Ni1 is lower than the second input shaft rotational speed Ni2, and as a result, the engine rotational speed Ne decreases before and after the shift. Therefore, simply switching the engagement state of the first clutch disk 41 and the second clutch disk 42 may increase the clutch load or cause a shift shock. Therefore, as described above, the shift control unit 3a performs the synchronization control to decelerate the engine speed Ne and synchronize with the first input shaft speed Ni1 before the first clutch disk 41 is completely connected. In addition, the engine speed Ne after shifting is stabilized.

  Further, for example, in a downshift such as a fifth gear to a fourth gear, assuming that the vehicle speed V before and after the gear shift is constant, the gear ratio of the gear shift gear is large. For this reason, the second input shaft rotational speed Ni2 is higher than the first input shaft rotational speed Ni1, thereby increasing the engine rotational speed Ne before and after the shift. Therefore, simply switching the engagement state of the first clutch disk 41 and the second clutch disk 42 may increase the clutch load or cause a shift shock. Therefore, before the second clutch disk 42 is completely connected, the shift control unit 3a performs synchronous control to increase the engine speed Ne and synchronize with the second input shaft speed Ni2, thereby reducing shift shock. The engine speed Ne after the shift is stabilized.

As shown in FIG. 1, the TCU 3 includes the above-described shift control unit 3a, required gear stage determination unit 3b, input shaft coaxial determination unit 3c, predicted vehicle acceleration calculation unit 3d, and shift method determination unit 3e.
When the shift command is sent as described above, the shift control unit 3a is disconnected from the engine 4 of the first input shaft 21 and the second input shaft 22 of the first clutch disk 41 and the second clutch disk 42. Disconnection control is performed to disconnect the clutch disk corresponding to the input shaft while controlling the clutch disk with a predetermined clutch torque Tc. At the same time, among the first clutch disk 41 and the second clutch disk 42, the clutch disk corresponding to the input shaft connected to the engine 4 of the first input shaft 21 and the second input shaft 22 is used as the clutch torque Tc. Then, while controlling to achieve the target clutch torque Tca, the engagement control is performed to synchronize and engage the engine speed Ne with the input shaft speed Ni of the input shaft to be connected.

  The target clutch torque Tca is calculated by the following [Equation 1]. This target clutch torque Tca controls the disengagement of the low-speed gear side clutch, and controls the disengagement control of the high-speed gear stage side clutch when engaging with the high speed gear side clutch. This is the reference transmission torque that enables a shift with suppressed shift shock when the low-speed gear stage clutch is controlled with this torque. The target clutch torque Tca is determined in advance every time the gear is shifted from a predetermined actual gear stage Gp to a predetermined required gear stage Gd (for example, 6th gear stage → 5th gear stage or 6th gear stage → 4th gear stage). Appropriate values are set by experiments or the like and stored in a ROM (not shown).

[Equation 1]
Tca = Te−Ie · ΔNet
Tca: target clutch torque Te: current output torque of the engine Ie: inertia ΔNet: target rotational speed variable speed

  Therefore, first, the inertia Ie (also referred to as the moment of inertia or the inertial performance ratio) of the engine 2 is multiplied by the target rotational speed variation ΔNet (corresponding to the target rotational speed variation of the present invention) of the engine 4 to obtain a high-speed gear stage side clutch. Alternatively, the target inertia torque Ie · ΔNet of the low speed gear stage side clutch is calculated. This “target inertia torque Ie · ΔNet” should be transmitted from the first and second clutch disks 41 and 42 to the drive shaft 4b of the engine 4 in order to suitably change (decelerate or accelerate) the engine speed Ne. It corresponds to deceleration torque or acceleration torque. In the above description, the target inertia torque Ie · ΔNet takes a negative value when decelerating the engine speed Ne, and takes a positive value when accelerating.

  The target speed change speed ΔNet is a value determined in advance as a target value for the speed change of the engine speed Ne in the upshift control (upshift) or the downshift control (downshift). That is, the target rotational speed change speed ΔNet is controlled so that the speed change shock can be suppressed and the speed change can be made early if the speed change of the engine speed Ne is controlled to the target rotational speed change speed ΔNet in the upshift control or the downshift control. Can be completed.

  Then, a target clutch torque Tca is calculated by subtracting the target inertia torque Ie · ΔNet from the current output torque Te of the engine 4. The “current output torque Te” of the engine 4 is, for example, the engine speed Ne detected by the prime motor speed detection unit 2b or the accelerator depression amount Lac of the accelerator pedal P detected by the accelerator depression amount detection unit 2a ( It can be calculated based on a detected value such as an accelerator opening.

  The clutch actuator operation amounts L1 and L2 of the first and second clutch actuators 17 and 18 for obtaining the target clutch torque Tca are calculated by a calculation unit (not shown) included in the shift control unit 3a. The correspondence relationship between the clutch actuator operation amount L and the clutch torque Tc is acquired in advance and stored, for example, in the ROM (see FIG. 4). In view of this, the calculation unit (not shown) obtains the clutch actuator operation amounts L1 and L2 of the first and second clutch actuators 17 and 18 corresponding to the target clutch torque Tca from the table of FIG.

  The requested gear stage determination unit 3b is a clutch in which the requested gear stage Gd sent from the TCU 3 is currently engaged among the first clutch disk 41 (first clutch) and the second clutch disk 42 (second clutch). It is determined whether or not it matches the actual gear stage Gp that is actually established on the input shaft corresponding to the disk. That is, it is confirmed that the required gear stage Gd has not yet been established as the actual gear stage Gp, and that shift control is performed toward the required gear stage Gd.

  The input shaft coaxial determination unit 3c corresponds to the request gear stage Gd and the actual gear stage Gp, respectively, when the request gear stage determination unit 3b determines that the request gear stage Gd does not match the actual gear stage Gp. Determine whether the input axes are the same. At this time, if the input shafts are the same, it indicates that the required gear stage Gd is deviated by two stages toward the low speed side with respect to the actual gear stage Gp. In such a state, when shifting the actual gear stage Gp (for example, 6th speed) toward the required gear stage Gd (for example, 4th speed), as shown in FIG. The second clutch disk 42 of the second clutch is controlled to be disconnected. At the same time, the first clutch disk 41 of the first clutch corresponding to the relay gear stage Gm (for example, the fifth speed) that is the transmission gear stage between the actual gear stage Gp and the required gear stage Gd is controlled. When the second clutch disk 42 is completely disconnected, the required gear stage Gd (for example, fourth gear) is engaged with the first countershaft 31 by the operation of the third shift clutch 103 (second shift mechanism). The required gear stage Gd is established with the second input shaft 22. Then, the second clutch second gear corresponding to the requested gear stage Gd (for example, fourth speed) is controlled while the first clutch disk 41 of the first clutch corresponding to the relay gear stage Gm (for example, fifth speed) is disconnected. Engagement control of the clutch disk 42 is performed. This completes the shift to the required gear stage Gd.

  The predicted vehicle acceleration calculation unit 3d shifts based on the detected accelerator depression amount Lac and the gear ratio of the requested gear stage Gd when the input shaft coaxial determination unit 3c determines that the corresponding input shafts are the same. A required gear stage predicted vehicle acceleration Gda, which is the acceleration of the vehicle at the subsequent required gear stage Gd, is calculated. That is, the engine speed Ne of the engine 4 requested by the driver is calculated based on the accelerator depression amount Lac of the accelerator pedal P that the driver has depressed, and the vehicle speed V is predicted and calculated from the engine speed Ne. The vehicle speed V predicted at this time is calculated based on the gear ratio of the required gear stage Gd. Then, the required gear stage predicted vehicle acceleration Gda requested by the driver is calculated from the map shown in FIG. 6 showing the correspondence between the vehicle speed V and the vehicle acceleration prepared in advance.

  Similarly, based on the detected accelerator depression amount Lac, the transmission gear ratio of the relay gear stage Gm, and the magnitude of the target clutch torque Tca to which the clutch corresponding to the relay gear stage Gm is engaged and controlled, A stage predicted vehicle acceleration Gma is calculated. Specifically, an average value Neav of the engine speed Ne while the relay gear stage Gm is engaged and controlled is calculated based on the target rotational speed change ΔNet based on the target clutch torque Tca that is changed according to the accelerator depression amount Lac. Then, the vehicle speed V while the relay gear stage Gm is engaged and controlled is predicted from the average value Neav of the engine speed Ne and the gear ratio of the relay gear stage Gm, and the vehicle at the relay gear stage is calculated from the map shown in FIG. The relay gear stage predicted vehicle acceleration Gma, which is the acceleration of, is calculated.

  The method of predicting the required gear stage predicted vehicle acceleration Gda and the relay gear stage predicted vehicle acceleration Gma is not limited to the method described above. For example, for the required gear stage predicted vehicle acceleration Gda, a target engine output torque Te is calculated based on the accelerator depression amount Lac. Then, the vehicle acceleration may be obtained from the driving force when the engine output torque Te is output to the drive wheels 16a and 16b via the required gear stage Gd having a predetermined gear ratio. Regarding the relay gear stage predicted vehicle acceleration Gma, the target clutch torque Tca controlled according to the accelerator depression amount Lac is transmitted to the drive wheels 16a and 16b via the relay gear stage Gm having a predetermined gear ratio. The vehicle acceleration may be obtained from the transmitted driving force.

  The speed change method determination unit 3e calculates a ratio (Gma / Gda) of the relay gear stage predicted vehicle acceleration Gma to the calculated required gear stage predicted vehicle acceleration Gda. Then, it is determined that the shift from the actual gear stage Gp to the requested gear stage Gd is performed via the relay gear stage Gm when the magnitude of the ratio (Gma / Gda) exceeds a predetermined threshold Gx. That is, when the ratio (Gma / Gda) exceeds the threshold value Gx, the relay gear stage predicted vehicle acceleration Gma of the vehicle that is traveling during the engagement control at the relay gear stage Gm is the value of the vehicle that is traveling at the required gear stage Gd. It shows that it is close to the required gear stage predicted vehicle acceleration Gda. Therefore, even if the speed is changed via the relay gear stage Gm as it is, a large torque reduction does not occur and there is no possibility that the driver feels a feeling of stickiness. The predetermined threshold Gx may be set in any way, but may be set by an experiment performed in advance. Further, the gear change performed via the relay gear stage Gm is a normal gear change method. That is, since the actual gear stage Gp and the relay gear stage Gm, and the relay gear stage Gm and the required gear stage Gd are established with different input shafts, the first clutch and the second clutch are, for example, the first clutch → the second clutch → The first clutch is sequentially connected to change gears.

  When the magnitude of the ratio (Gma / Gda) is smaller than the predetermined threshold Gx, it is determined that the shift control is performed without using the relay gear stage Gm. As a specific control method that is performed without using the relay gear stage Gm, a so-called single speed change can be mentioned (see FIG. 8). In the single speed change, first, the second gear corresponding to the actual gear stage Gp (for example, sixth gear) is disengaged, and then the actual gear stage Gp is released. Then, after the required gear stage Gd corresponding to the same input shaft (for example, the second input shaft 22) as the actual gear stage Gp is established on the second input shaft 22, the input shaft rotational speed Ni2 and the engine rotational speed Ne are obtained. The corresponding clutch (second clutch) is synchronized and engaged by controlling the engagement. At this time, the engine rotational speed Ne is controlled by various methods to increase the rotational speed, and the input shaft of the input shaft (second input shaft 22) whose rotational speed has increased due to the establishment of the required gear stage Gd. The rotational speed Ni2 and the engine rotational speed Ne can be synchronized in a short time. As a specific method for increasing the engine speed Ne, the amount of air supplied to the engine 4 controlled by the throttle body is increased and the fuel injection amount of the injector is increased. At this time, the engine rotational speed Ne is monitored by the prime mover rotational speed detector 2b, and the input shaft rotational speed Ni is controlled while being monitored by the first and second input shaft rotational speed sensors 24a and 24b. However, any control for increasing the engine speed Ne may be used.

In the above description, the difference (difference) between the required gear stage Gd and the actual gear stage Gp is two stages (for example, 6th speed and 4th speed, 5th speed and 3rd speed, etc.) instead of the input shaft coaxial determination unit 3c. You may make it confirm. This also confirms that the input shafts corresponding to the required gear stage Gd and the actual gear stage Gp are the same.
Moreover, it is good also as an aspect which does not provide the input-axis coaxial determination part 3c as another Example. At this time, when the required gear stage Gd and the actual gear stage Gp are determined to be coincident by the required gear stage determination unit 3b, the predicted vehicle speed calculation unit 3d and the predicted gear stage predicted vehicle acceleration Gda and the relay gear stage prediction are determined. The vehicle acceleration Gma is calculated. However, in this case, the number of deviation stages between the required gear stage Gd and the actual gear stage Gp is unknown. As described above, when the control is continued in a state where the number of divergence stages between the required gear stage Gd and the actual gear stage Gp is unknown, there is a case where the difference between the requested gear stage Gd and the actual gear stage Gp is only one stage. . At that time, the relay gear stage predicted vehicle acceleration Gma cannot be calculated because there is no relay gear stage Gm. Therefore, it is assumed that the control is stopped when it becomes clear that the calculation of the relay gear stage predicted vehicle acceleration Gma cannot be performed. When the calculation in the predicted vehicle acceleration calculation unit 3d, which can be performed only when the relay gear stage Gm is provided in the subsequent control, is completed, the control after the shift method determination unit 3e is performed.

Next, the shift control method and operation of the shift control device provided in the dual clutch automatic transmission 1 according to the first embodiment in a traveling vehicle will be described based on the time charts of FIGS. 7 and 8 and the flowchart of FIG. To do.
In the present embodiment, for example, the vehicle is accelerating, the second clutch disk 42 (second clutch) is engaged, and the second input shaft 22 and the engine 4 are connected. To do. At this time, the vehicle is traveling by the sixth speed gear stage established by the second input shaft 22. Therefore, the sixth gear is the actual gear Gp. Then, the driver desires acceleration and depresses the accelerator pedal P by a predetermined accelerator depression amount Lac, whereby the accelerator opening is downshifted to the fifth gear and the fourth gear as shown by the one-dot chain line in FIG. A description will be given on the assumption that a shift request from the TCU 3 to the fourth speed gear stage (requested gear stage Gd) that deviates two stages from the actual gear stage Gp to the low speed side by passing through the transmission lines D and C will be described.

  Further, in the present embodiment, the actual gear stage Gp and the required gear stage Gd are separated by two stages. For example, the normal shift state of the dual clutch 40 from the sixth gear stage to the fourth gear stage is shown in the torque column of FIG. As shown. Specifically, the first input shaft 21 is established after the start of the separation control of the sixth gear (actual gear Gp) until the shift to the fourth gear (requested gear Gd). Via a fifth gear (relay gear stage Gm). The dual clutch 40 is controlled by the preset target clutch torque Tca up to a predetermined position until shifting to the fourth gear (required gear stage Gd). The so-called half-clutch state is maintained in the first clutch disk 41 and the second clutch disk 42 by the target clutch torque Tca controlled in this way. As a result, the engine speed Ne rises and increases at a predetermined speed change speed ΔNet. Then, the increased engine rotational speed Ne is eventually synchronized with the input shaft rotational speed Ni of the second input shaft 22 increased by downshifting to the fourth gear (required gear stage Gd), and the shift is completed. . Such a shift will be described below as a normal shift control method.

As shown in the flowchart of FIG. 9, in step S10 (required gear stage determination step), it is confirmed whether or not there is a downshift command. In the present embodiment, since there is a downshift gear change command, the process moves to step S12. If there is no shift command, step S10 is repeatedly processed until the downshift command is sent.
In step S12 (required gear stage determining step), it is determined whether or not the requested gear stage Gd and the actual gear stage Gp are the same. In the present embodiment, the fourth speed gear stage (required gear stage Gd) and the sixth speed gear stage (actual gear stage Gp) do not coincide with each other, and the process moves to step S14. If they match, the shift to the required gear stage Gd has already been completed, and the process returns to step S10.

  In step S14 (input shaft coaxial determination step), when it is determined in the required gear stage determination step that the required gear stage Gd does not coincide with the actual gear stage Gp, each of the required gear stage Gd and the actual gear stage Gp is determined. It is determined whether the corresponding input axes are the same. In this embodiment, since the input shafts corresponding to each are the second input shafts 22 and are the same, the process moves to step S18. If they do not match, it indicates that the input shaft corresponding to the required gear stage Gd is different from the input shaft corresponding to the actual gear stage Gp, and this is a normal dual clutch shift, so step S18. Then, normal shift control is performed and the program is terminated.

  As described above, in step S14, instead of the input shaft coaxial determination step, for example, it may be confirmed that there are two divergences between the required gear stage Gd and the actual gear stage Gp. If the deviation is two steps, the process moves to step S20, and if the deviation is not two steps but one step, normal shift control is performed in step S18 and the program is terminated.

  Furthermore, step S14 may be abolished as described above as another embodiment. The control at this time is as described above, and when the difference between the required gear stage Gd and the actual gear stage Gp is only one stage, the relay gear stage Gm does not exist. Therefore, the calculation of the relay gear stage predicted vehicle acceleration Gman is stopped in the following step S16, and then the normal shift control is performed in step S18 and the program is terminated. At this time, the difference in the number of gears between the required gear stage Gd and the actual gear stage Gp has not been confirmed. However, for example, the relay gear stage Gm that should have a difference from the required gear stage Gd is one stage. When they coincide with each other, it may be determined that there is no relay gear stage Gm and the calculation is stopped. If the difference between the required gear stage Gd and the actual gear stage Gp is two and has the relay gear stage Gm, the required gear stage predicted vehicle acceleration Gda and the relay gear stage predicted vehicle acceleration are determined in step S16. Gma can be calculated. For this reason, after calculating the required gear stage predicted vehicle acceleration Gda and the relay gear stage predicted vehicle acceleration Gma, the program moves to the following step S20 to continue the program. A corresponding effect can be obtained by such a method.

  In step S16 (predicted vehicle acceleration calculation step), the required gear stage predicted vehicle acceleration Gda and the relay gear stage predicted vehicle acceleration Gma are calculated based on the above-described calculation method (see the vehicle acceleration column in FIG. 7).

  In step S20 (shifting method determination step), the ratio (Gma / Gda) of the relay gear predicted vehicle acceleration Gma to the required gear predicted vehicle acceleration Gda is calculated. If it is determined that the ratio (Gma / Gda) exceeds the predetermined threshold Gx, the process proceeds to step S22. If it is determined that the ratio (Gma / Gda) is smaller than the predetermined threshold Gx, the process proceeds to step S24.

  In step S22, shifting from the actual gear stage Gp to the requested gear stage Gd is performed via the relay gear stage Gm. That is, the shift control is performed by the control normally performed when the actual gear stage Gp and the required gear stage Gd described above are separated by two stages. When the ratio (Gma / Gda) exceeds the threshold value GX, the predicted vehicle relay gear speed Gma of the vehicle at the relay gear stage Gm is close to the predicted required gear speed vehicle acceleration Gda of the vehicle at the required gear stage Gd. Therefore, even if the speed is changed via the relay gear stage Gm as it is, a large torque reduction does not occur and there is no possibility that the driver feels a feeling of tapping.

  In step S24, the shift control is performed by the single shift described above without using the relay gear stage Gm (see FIG. 8). As a result, it is possible to complete the switching to the required gear stage Gd in a short time and obtain the required gear stage predicted vehicle acceleration Gda, and also to shift without the relay gear stage Gm determined that the vehicle acceleration is small. There is no risk that the driver will feel a sense of acceleration.

  In the present embodiment, the speed change method determination unit 3e performs the single shift and the normal relay gear stage Gm based on the ratio (Gma / Gda) of the relay gear stage predicted vehicle acceleration Gma to the required gear stage predicted vehicle acceleration Gda. Via control. However, the present invention is not limited to this, and the selection between the single speed change and the control via the normal relay gear stage Gm may be determined based on the absolute value of the relay gear stage predicted vehicle acceleration Gma. That is, when the absolute value of the relay gear stage predicted vehicle acceleration Gma is larger than the predetermined threshold value, control is performed via the normal relay gear stage Gm, and when the absolute value is smaller than the predetermined threshold value, the single value not via the relay gear stage Gm is executed. Shifting may be performed. However, at this time, the magnitude of the absolute value of the relay gear stage predicted vehicle acceleration Gma differs depending on the vehicle speed and the transmission gear stage. For this reason, a predetermined threshold may be provided in accordance with the vehicle speed and the transmission gear stage. This also provides the same effect.

  As is apparent from the above description, in the dual clutch automatic transmission 1 according to the present embodiment, the requested gear stage determination unit 3b is engaged when a shift command is sent by the downshift requested gear stage Gd. It is determined that the actual gear stage Gp established on the input shaft corresponding to the clutch in the state does not match the requested gear stage Gd, and the input shaft coaxial determination unit 3c corresponds to the requested gear stage Gd and the actual gear stage Gp, respectively. If it is determined that the input shafts are the same, the predicted vehicle acceleration calculation unit 3d calculates the required gear stage predicted vehicle acceleration Gda of the required gear stage Gd and the relay gear stage predicted vehicle acceleration Gma of the relay gear stage Gm. Thus, after the input shaft coaxial determination unit 3c determines that the required gear stage Gd and the actual gear stage Gp are separated by two stages and has the relay gear stage Gm, the predicted vehicle acceleration calculation unit 3d requests Since the gear stage predicted vehicle acceleration Gda and the relay gear stage predicted vehicle acceleration Gma are calculated, there is no waste and it is efficient.

  The required gear stage predicted vehicle acceleration Gda is calculated based on the detected accelerator depression amount Lac and the speed ratio of the required gear stage Gd. Further, the relay gear stage predicted vehicle acceleration Gma is calculated based on the detected accelerator depression amount Lac, the transmission gear ratio of the relay gear stage Gm, and the magnitude of the target clutch torque Tca at which the relay gear stage Gm is engaged and controlled. . Then, the speed change method determination unit 3e determines the relay gear stage Gm in the shift from the actual gear stage Gp to the required gear stage Gd according to the relationship between the calculated required gear stage predicted vehicle acceleration Gda and the relay gear stage predicted vehicle acceleration Gma. It is determined whether or not. In this way, since the predicted vehicle acceleration Gma of the relay gear stage Gm is actually calculated to determine the influence of the relay gear stage Gm, it is possible to eliminate the case where a feeling of torque fluctuation is generated with high accuracy.

In the present embodiment, the speed change method determination unit 3e calculates a ratio (Gma / Gda) of the relay gear predicted vehicle acceleration Gma to the required gear predicted vehicle acceleration Gda. When the magnitude of the ratio (Gma / Gda) exceeds a predetermined threshold Gx, it is determined that the shift from the actual gear stage Gp to the required gear stage Gd is performed via the relay gear stage Gm. That is, when the relay gear stage predicted vehicle acceleration Gma has a ratio of a certain value or more with respect to the required gear stage predicted vehicle acceleration Gda, the driver does not react to the acceleration even if shifting is continued through the relay gear stage Gm. There is no risk of feeling sticky. As a result, the control is performed with the relay gear stage Gm, which is a normal control, interposed in the shift from the actual gear stage Gp separated by two stages to the required gear stage Gd.
When the ratio is smaller than the predetermined threshold Gx, the relay gear predicted vehicle acceleration Gma does not have a certain ratio or more with respect to the required gear predicted vehicle acceleration Gda. For this reason, if the speed is changed via the relay gear stage Gm, the driver may feel a sense of acceleration due to the torque reduction. Therefore, a shift from the actual gear stage Gp separated by two stages to the required gear stage Gd is performed by the above-described single shift without interposing the relay gear stage Gm. As a result, it is possible to complete the switching to the required gear stage Gd in a short time and obtain the required gear stage predicted vehicle acceleration Gda, and also to shift without the relay gear stage Gm determined that the vehicle acceleration is small. There is no risk that the driver will feel a sense of acceleration.

  In the present embodiment, 51, 53, 55 and 57 are fixedly provided on the first input shaft 21 with odd-numbered drive gears, and the even-numbered drive gears 52, 54, And 56 were fixed. The first countershaft 31 and the second countershaft 32 mesh with the odd-numbered drive gears of the first input shaft 21 to establish odd-numbered gears, and the second input shaft 22 The driven gears 62, 64, and 66 that mesh with the even-numbered drive gears to establish the even-numbered gears are provided so as to be free-wheeling. However, the present invention is not limited to this, and the drive gears 51, 53, 55, and 57 and the drive gears 52, 54, and 56 may be provided on the first input shaft 21 and the second input shaft 22 so as to be free to rotate. At this time, the first to seventh speed driven gears 61 to 67 may be fixedly provided on the first countershaft 31 and the second countershaft 32.

  Further, like the dual clutch automatic transmission disclosed in FIG. 1 of Japanese Patent Application Laid-Open No. 2011-144882, only the seventh speed drive gear 26a is provided on the first input shaft 15 so as to be free-wheeling and meshed with the seventh speed drive gear 26a. The seventh speed driven gear 26b may be fixed to the second countershaft 18. Further, as shown in FIG. 1 of the publication, the first input shaft 15 and the output shaft 19 may be directly connected by moving the switching clutch 30D to the right side of the drawing. The same effect can be obtained in such a dual clutch type automatic transmission.

  The arrangement of the first and second clutch disks 41 and 42, the center plate 43, and the first and second pressure plates 44 and 45 constituting the dual clutch 40 according to this embodiment will be described in this embodiment. However, the present invention is not limited to this mode and may be arranged in any way.

  In the present embodiment, the dual clutch automatic transmission having the seventh forward speed is described as the dual clutch automatic transmission according to the present invention. However, the present invention is not limited to this mode, and the dual clutch automatic transmission may have a forward shift speed exceeding 7th speed or a forward shift speed not exceeding 6th speed. This also provides the same effect.

In the present embodiment, four fork shafts 135 are provided, and the forks 72a to 72d provided for the respective fork shafts 135 are operated to switch the gear stages. However, the present invention is not limited to this, and a selection motor may be provided, the fork shaft may be selected by driving the selection motor, and the selected fork shaft may be slid by the shift motor to switch each gear stage.
Further, the dual clutch type automatic transmission may be applied to other automatic transmissions such as motorcycles, instead of being applied to automobiles.

DESCRIPTION OF SYMBOLS 1 ... Dual clutch type automatic transmission, 2 ... Transmission control unit (ECU), 3 ... Transmission control unit (TCU), 4 ... Engine, 4a ... Output shaft rotation speed sensor, 10 ... Case, 11 ... Mission case, 12 ... Clutch housing, 17 ... First clutch actuator, 18 ... Second clutch actuator, 21 ... First input shaft, 22 ... Second input shaft, 23a, 23b ... vehicle speed sensor, 27 ... accelerator opening sensor, 40 ... dual clutch, 41 ... first clutch disc, 42 ... second clutch disc, 101, 104 ... 1st shift mechanism (1st, 4th shift clutch), 102, 103 ... 2nd shift mechanism (2nd, 3rd shift clutch), Gd ... Required gear stage, Gm ... Relay gi Ya stage, Gp ... real gear stage, Ne ... engine speed, P ... accelerator pedal.

Claims (3)

A first input shaft and a second input shaft arranged concentrically;
A dual clutch having a first clutch for transmitting a rotational driving force of a motor of a vehicle to the first input shaft and a second clutch for transmitting the rotational driving force to the second input shaft;
A first shift mechanism that shifts the rotational driving force transmitted to the first input shaft to establish an odd-numbered shift stage, and a gear that shifts the rotational driving force transmitted to the second input shaft to change an even-numbered shift stage. A second shift mechanism to be established;
An accelerator depression amount detection unit for detecting the accelerator depression amount of the accelerator;
When a shift command is sent, it corresponds to the input shaft of the first clutch and the second clutch that establishes the actual gear stage separated from the prime mover of the first input shaft and the second input shaft. input shaft clutch, row a disconnection control for dissecting by controlling the clutch torque Utotomoni, required gear stage in which the connected to a prime mover of said first input shaft and the second input shaft is established the clutch corresponding to, and a shift control device for performing engagement control to engage by controlling the clutch torque,
The shift control device includes:
Whether the required gear stage when the required gear stage downshift in the gear shift command is transmitted is consistent with the actual gear stage that is actually established in the input shaft which corresponds to the clutch that is currently engaged A request gear stage determination unit for determining;
When the required gear stage determination unit determines that the required gear stage does not coincide with the actual gear stage, the post-shift gear change based on the detected accelerator depression amount and the speed ratio of the required gear stage The required gear stage predicted vehicle acceleration of the vehicle at the required gear stage is calculated, and the detected accelerator depression amount , the gear ratio of the relay gear stage that is a shift gear stage between the required gear stage and the actual gear stage , and the relay gear size of the goal clutch torque calculated based on the target speed shift degree output driving force of the prime mover is a clutch torque to be required for the prime mover as it is the engagement control Based on this, the predicted vehicle acceleration performance for calculating the predicted vehicle acceleration of the relay gear of the vehicle when the engagement gear is controlled to be engaged by the target clutch torque. And parts,
In the shift from the actual gear stage to the required gear stage when the calculated relay gear stage predicted vehicle acceleration has a ratio equal to or higher than a certain ratio to the calculated required gear stage predicted vehicle acceleration. When it is determined that the relay gear stage is passed, and the relay gear stage predicted vehicle acceleration does not have a ratio greater than or equal to the predetermined gear stage predicted vehicle acceleration, the actual gear stage is changed to the required gear stage. A speed change method determination unit for determining that the intermediate gear stage is not passed in
Dual-clutch automatic transmission with Oite to claim 1,
The shift control device has input shafts respectively corresponding to the requested gear stage and the actual gear stage when the requested gear stage determining unit determines that the requested gear stage does not match the actual gear stage. A dual clutch automatic transmission including an input shaft coaxial determination unit that determines whether or not they are the same. A first input shaft and a second input shaft that are concentrically arranged, a first clutch that transmits a rotational driving force of a prime mover of a vehicle to the first input shaft, and a second clutch that transmits the rotational driving force to the second input shaft. A dual clutch having two clutches, a first shift mechanism that shifts the rotational driving force transmitted to the first input shaft to establish an odd speed, and the rotational driving force transmitted to the second input shaft A second shift mechanism that establishes an even-numbered speed stage, an accelerator depression amount detection unit that detects an accelerator depression amount of the accelerator, and when a shift command is sent, of the first clutch and the second clutch the clutch corresponding to the input shaft of actual gear stage is decoupled from said prime mover of said first input shaft and the second input shaft is established, for dissecting by controlling the clutch torque switching Control lines as the Utotomoni engagement by a clutch corresponding to the input shaft required gear stage in which the connected to a prime mover of said first input shaft and the second input shaft is established, to control the clutch torque A shift control device for a dual clutch type automatic transmission comprising a shift control device for performing engagement control,
The shift control method includes:
Whether the required gear stage when the required gear stage downshift in the gear shift command is transmitted is consistent with the actual gear stage that is actually established in the input shaft which corresponds to the clutch that is currently engaged A required gear stage determination step for determining;
When the requested gear stage determination step determines that the requested gear stage does not match the actual gear stage, based on the detected accelerator depression amount and the speed ratio of the requested gear stage, The required gear stage predicted vehicle acceleration of the vehicle at the required gear stage is calculated, and the detected accelerator depression amount , the gear ratio of the relay gear stage that is a shift gear stage between the required gear stage and the actual gear stage , and the relay gear size of the goal clutch torque calculated based on the target speed shift degree output driving force of the prime mover is a clutch torque to be required for the prime mover as it is the engagement control Based on the estimated vehicle acceleration for calculating the predicted vehicle acceleration of the relay gear of the vehicle when the engagement of the relay gear is controlled by the target clutch torque. And the degree calculation step,
In the shift from the actual gear stage to the required gear stage when the calculated relay gear stage predicted vehicle acceleration has a ratio equal to or higher than a certain ratio to the calculated required gear stage predicted vehicle acceleration. When it is determined that the relay gear stage is passed, and the relay gear stage predicted vehicle acceleration does not have a ratio greater than or equal to the predetermined gear stage predicted vehicle acceleration, the actual gear stage is changed to the required gear stage. A speed change method determination step for determining that the relay gear stage is not passed in the speed change of
A shift control method for a dual clutch automatic transmission comprising:

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