JP2015078765A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable the automatic gear change of a second transmission, in a power transmission device comprising the second transmission which is interposed between a stepped first transmission and has an engaging clutch.SOLUTION: A power transmission device comprises a second transmission 40 having a planetary gear mechanism 45 in which a ring gear 47 and a planetary carrier 49 are connected to an output shaft 27 of a first transmission 25 and drive wheels, a dog clutch 50 which performs the connection and release of the ring gear 47 and the planetary carrier 49, and a two-way clutch 52 interposed between a sun gear 46 of the planetary gear mechanism 45 and a transmission case 22. The two-way clutch 52 regulates the rotation of the sun gear 46 in a direction opposite to the ring gear 47 at forward traveling. When the dog clutch 50 is released, and a pedal-in amount of an accelerator pedal is reduced, the second transmission 40 is gear-changed by being engaged with the dog clutch 50 accompanied by a decrease of a rotation number of the ring gear 47 and an increase of a rotation number of the sun gear 46.

Description

  The present invention relates to a power transmission device, and more particularly to a power transmission device that is mounted on a vehicle and transmits power from a prime mover to an axle.

  Conventionally, a power transmission device of this type has been proposed that includes a main transmission connected to the output shaft of the engine and a sub-transmission connected to the output shaft of the main transmission (for example, Patent Document 1). In this power transmission device, the sub-transmission includes a planetary gear mechanism in which a sun gear is fixed to a main shaft of a main transmission and a planet carrier that supports a plurality of planet gears is connected to an output shaft, and a planetary gear mechanism. A sleeve that is integrated with the outer ring gear and has a spline formed on the inner peripheral surface thereof and can be displaced in the axial direction, and a first spline that is disposed on one side of the sleeve in the axial direction and integrated with the transmission case And a second spline disposed on the other axial side of the sleeve and integrated with the output shaft. Then, the sleeve is displaced in the axial direction, and the spline of the sleeve meshes with the first or second spline, thereby executing a shift.

  In addition, an automatic transmission having an automatic transmission mechanism (stepped transmission mechanism) mounted on a vehicle and connected to an output shaft of a drive source (engine), a propeller shaft and the like connected to the output shaft of the automatic transmission mechanism There is also proposed a transmission (stepped transmission) that is connected to a drive wheel via a drive wheel and has two speed stages, a high speed stage and a low speed stage (see, for example, Patent Document 2). In this power transmission device, when the transfer switching lever is switched by the driver during traveling, the clutch and brakes according to the shift stage of the automatic transmission are released to transmit power between the drive source and the drive wheels of the automatic transmission. Is switched, and the shift stage of the transfer is switched, and then the shift stage of the automatic transmission is set to a shift stage according to the shift stage of the transfer. With such control, it is possible to switch the shift speed of the transfer during traveling.

JP 2010-91070 A JP 2003-166565 A

  In such a power transmission device, a meshing clutch is used as a sub-transmission clutch in the same manner as in the former power transmission device, thereby suppressing a reduction in efficiency due to drag loss or the like as compared with a configuration using a friction engagement element. be able to. However, when the mesh clutch is used, generally, as in the latter power transmission device, the transfer is shifted only by the operation of the transfer switching lever by the driver. For this reason, it is a problem how to perform automatic shift of the transfer while traveling (shift not depending on the operation of the driver's lever).

  A power transmission device according to the present invention includes a second transmission that is interposed between a stepped first transmission and an axle and has a meshing clutch, and enables automatic transmission of the second transmission. Main purpose.

  The power transmission device of the present invention employs the following means in order to achieve the main object described above.

The power transmission device of the present invention is
A power transmission device mounted on a vehicle and transmitting power from a prime mover to an axle,
A stepped first transmission connected to the output shaft of the prime mover;
A two-stage second transmission connected to the output shaft of the first transmission and the axle;
Control means for controlling the first transmission and the second transmission;
With
The second transmission includes a planetary gear mechanism having a first rotation element connected to an output shaft of the first transmission, a second rotation element connected to the axle, and a third rotation element; A meshing clutch that connects and disconnects two of the rotating element, the second rotating element, and the third rotating element, and at least the first direction in a direction opposite to the rotating direction of the first rotating element during forward traveling. A rotation restricting means capable of restricting the rotation of the three-rotating element, and a gear position on the low vehicle speed side is formed by releasing the meshing clutch, and a gear stage on the high vehicle speed side is formed by engaging the meshing clutch. Configured,
The control means engages the meshing clutch when the accelerator depression amount is reduced during traveling forward with the meshing clutch being released.
This is the gist.

  In the power transmission device of the present invention, the planetary gear mechanism of the second transmission includes a first rotation element connected to the output shaft of the first transmission, a second rotation element connected to the axle, and a third rotation element. Have Then, during forward traveling, the connection between the first rotating element, the second rotating element, and the third rotating element of the planetary gear mechanism is released by releasing the meshing clutch. Therefore, by restricting the rotation of the third rotating element in the direction opposite to the rotating direction of the first rotating element during forward travel by the rotation restricting means, the second transmission transmits the power of the output shaft of the first transmission. It is transmitted to the axle with a reduction in the rotational speed and an increase in torque (forms a shift stage on the low vehicle speed side). On the other hand, during forward travel, the engagement of the mesh clutch causes the three rotation elements to rotate together by connecting two of the first rotation element, the second rotation element, and the third rotation element of the planetary gear mechanism. . Therefore, in the second transmission, the power of the output shaft of the first transmission is transmitted to the axle while maintaining the rotational speed and torque (forms a shift stage on the high vehicle speed side). In the power transmission device of the present invention, the meshing clutch is engaged when the amount of accelerator depression decreases while the meshing clutch is released and the vehicle is traveling forward. Specifically, when the accelerator depression amount decreases and the rotation speed of the output shaft of the first transmission, that is, the rotation speed of the first rotation element decreases, the rotation speed of the third rotation element increases accordingly. When the element, the second rotating element, and the third rotating element have substantially the same rotational speed, the meshing clutch is engaged. Accordingly, the automatic transmission of the second transmission (shift from the low vehicle speed side gear stage to the high vehicle speed side gear stage) can be performed during traveling. From the above, at the time of starting, acceleration can be improved at the low speed side gear stage, and after engagement of the meshing clutch, fuel efficiency can be improved at the high speed side gear stage. . Even when the amount of accelerator depression is reduced while the meshing clutch is released and the vehicle is traveling forward, the meshing clutch may not be engaged when the gear position of the first transmission is equal to or lower than the predetermined gear position. .

  In such a power transmission device of the present invention, after the engagement of the engagement clutch, the control means can hold the engagement of the engagement clutch until the vehicle stops. If it carries out like this, after engaging a meshing clutch, it can drive | work at the gear stage of the high vehicle speed side until a vehicle stops.

  Further, in the power transmission device according to the present invention, when the accelerator depressing amount is reduced during the forward traveling with the meshing clutch released, the control means reduces the rotational speed of the first rotating element. The meshing clutch is engaged when the rotation speed of the third rotation element increases and the first rotation element, the second rotation element, and the third rotation element reach substantially the same rotation speed. It can also be.

  Furthermore, in the power transmission device of the present invention, the rotation restricting means may be capable of restricting bidirectional rotation of the third rotating element. In this case, when the accelerator depression amount is reduced while the meshing clutch is released and the vehicle is traveling forward, the rotational speed of the third rotating element is increased by restricting the bidirectional rotation of the third rotating element. It is possible to regulate (approaching the rotation speed of the first rotation element). As a result, the engine brake can be applied to the axle (drive wheel).

  Alternatively, in the power transmission device of the present invention, the rotation restricting means is configured as a two-way clutch capable of restricting the rotation of the third rotating element in a direction opposite to the rotating direction of the first rotating element according to a shift position. The control means may be configured to engage the meshing clutch when the accelerator depression amount is reduced while the meshing clutch is released and traveling forward or backward. In this way, the automatic transmission of the second transmission (shift from the low vehicle speed side gear stage to the high vehicle speed side gear stage) can be performed during traveling not only during forward travel but also during reverse travel.

  In addition, in the power transmission device of the present invention, the rotation restricting means includes a one-way clutch that restricts the rotation of the third rotating element in a direction opposite to the rotating direction of the first rotating element during forward traveling, and the one-way clutch A second meshing clutch interposed between a clutch and a case housing the second transmission, and the control means engages the meshing clutch and releases the second meshing clutch during reverse travel. Can also be.

  Further, in the power transmission device of the present invention, the rotation restricting means includes a one-way clutch that restricts rotation of the third rotating element in a direction opposite to the rotating direction of the first rotating element during forward traveling, The meshing clutch includes a first state in which the third rotating element is not connected to the first rotating element or the second rotating element or a case housing the second transmission, and the third rotating element is connected to the first rotating element. A second state in which the rotating element or the second rotating element is connected and a third state in which the third rotating element is non-rotatably connected to the case are configured to be switchable. When the meshing clutch is in the first state, a low-speed side shift stage for forward travel is formed, and when the meshing clutch is in the second state, a high-speed side shift stage for forward traveling is formed. And, the dog clutch is configured to form a gear stage for reverse travel by a third state, it may be a thing.

It is a block diagram which shows the outline of a structure of the motor vehicle 10 carrying the power transmission device 20 as one Example of this invention. FIG. 2 is a configuration diagram showing an outline of the configuration of a power transmission device 20. It is explanatory drawing which shows the operation table showing the relationship between each gear stage of the 1st transmission 25, and the operation state of clutch C1-C4, brake B1, B2, and one-way clutch F1. FIG. 6 is an explanatory diagram illustrating a velocity diagram illustrating the relationship between the rotational speeds of the rotating elements that constitute the first transmission 25. FIG. 6 is an explanatory diagram illustrating a speed diagram illustrating the relationship between the rotational speeds of forward travel between rotating elements constituting the second transmission 40; It is explanatory drawing which shows the reduction ratio of the power transmission device 20 (the 1st transmission 25 and the 2nd transmission 40). It is a block diagram which shows the outline of a structure of the power transmission device 120 of a modification. It is a block diagram which shows the outline of a structure of the power transmission device 240 of a modification. FIG. 8 is an explanatory diagram illustrating a speed diagram illustrating the relationship between the rotational speeds of rotating elements that constitute the second transmission 240.

  Next, the form for implementing this invention is demonstrated using an Example.

  FIG. 1 is a configuration diagram showing an outline of the configuration of an automobile 10 equipped with a power transmission device 20 as an embodiment of the present invention, and FIG. 2 is a configuration diagram showing an outline of the configuration of the power transmission device 20. . The automobile 10 of the embodiment is configured as a rear wheel drive vehicle. As shown in FIG. 1, an engine 12 as a prime mover, and an engine electronic control unit (hereinafter referred to as an engine ECU) 14 for controlling the engine 12, A brake electronic control unit (hereinafter referred to as a brake ECU) 15 for controlling an electronically controlled hydraulic brake unit (not shown), and power for transmitting power from the engine 12 to a drive wheel (rear wheel) DW via a differential gear 80 And a transmission device 20. The engine ECU 14, the brake ECU 15, and the speed change ECU 21 of the power transmission device 20 are connected to each other via a communication port, and exchange various control signals and data necessary for control.

  Although not shown, the engine ECU 14 is configured as a microprocessor centered on a CPU, and includes a ROM for storing a processing program, a RAM for temporarily storing data, an input / output port, and a communication port in addition to the CPU. . The engine ECU 14 includes an accelerator opening Acc from an accelerator pedal position sensor 92 that detects the depression amount (operation amount) of the accelerator pedal 91, a vehicle speed V from a vehicle speed sensor 98 that detects a vehicle speed, and a rotation of the crankshaft 13 of the engine 12. A crank angle θcr or the like from a crank position sensor that detects the position is input via an input port. The engine ECU 14 outputs a drive control signal to the throttle motor that drives the throttle valve, a drive control signal to the fuel injection valve, an ignition control signal to the spark plug, and the like via the output port. The engine ECU 14 calculates the rotational speed of the crankshaft 13, that is, the rotational speed Ne of the engine 12 based on the crank angle θcr from the crank position sensor attached to the crankshaft 13.

  Although not shown, the brake ECU 15 is configured as a microprocessor centered on a CPU, and includes a ROM for storing a processing program, a RAM for temporarily storing data, an input / output port, and a communication port in addition to the CPU. . The brake ECU 15 receives a master cylinder pressure from a master cylinder pressure sensor 94 that detects a master cylinder pressure (depression force of the brake pedal 93), a vehicle speed V from a vehicle speed sensor 98, and the like. A drive signal to the brake actuator of the hydraulic brake unit is output via the output port.

  1 and 2, the power transmission device 20 includes a starting device (fluid transmission device) 23, an oil pump 24, a first transmission 25, a second transmission 40, a hydraulic control device 60, a parking lock (not shown). It has a mechanism, a transmission case 22 for housing them, a shift electronic control unit (hereinafter referred to as a shift ECU) 21 for controlling the entire apparatus, and the like.

  The starting device 23 includes an input-side pump impeller 23p connected to the crankshaft of the engine 12, an output-side turbine runner 23t, a pump impeller 23p connected to the input shaft (input member) 26 of the first transmission 25, A stator 23s that is arranged inside the turbine runner 23t and rectifies the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotational direction of the stator 23s to one direction, a lock-up clutch 23c, and a damper mechanism It is configured as a torque converter having 23d and the like. The starting device 23 may be configured as a fluid coupling that does not have the stator 23s.

  The oil pump 24 is a gear pump having a pump assembly including a pump body and a pump cover, an external gear connected to the pump impeller 23p of the starting device 23 through a hub, an internal gear meshing with the external gear, and the like. It is configured. The oil pump 24 is driven by power from the engine 12, sucks hydraulic oil (ATF) stored in a hydraulic oil storage unit (not shown), and pumps it to the hydraulic control device 60.

  The first transmission 25 is configured as an eight-speed transmission, and in addition to the input shaft 26, an output shaft (output member) 27 connected to the input shaft 41 of the second transmission 40, and a double Pinion type first planetary gear mechanism 30, Ravigneaux type second planetary gear mechanism 35, four clutches C1, C2, C3, C4 and two brakes B1 for changing the power transmission path from the input side to the output side , B2, and a one-way clutch F1.

  The first planetary gear mechanism 30 of the first transmission 25 is engaged with a sun gear 31 that is an external gear and a ring gear 32 that is an internal gear arranged concentrically with the sun gear 31 and one of them is a sun gear 31. In addition, the other has a planetary carrier 34 that holds a plurality of sets of two pinion gears 33a and 33b meshing with the ring gear 32 so as to be rotatable (rotatable) and revolved. The sun gear 31 of the first planetary gear mechanism 30 is fixed to the transmission case 22, and the planetary carrier 34 of the first planetary gear mechanism 30 is connected to the input shaft 26 so as to be integrally rotatable. The first planetary gear mechanism 30 is configured as a so-called reduction gear, and decelerates the power transmitted to the planetary carrier 34 as an input element and outputs it from a ring gear 32 as an output element.

  The second planetary gear mechanism 35 of the first transmission 25 is an internal gear arranged concentrically with the first sun gear 36a and the second sun gear 36b, which are external gears, and the first and second sun gears 36a and 36b. A ring gear 37, a plurality of short pinion gears 38a meshing with the first sun gear 36a, a plurality of long pinion gears 38b meshing with the second sun gear 36b and the plurality of short pinion gears 38a and meshing with the ring gear 37, and a plurality of short pinion gears 38a And a planetary carrier 39 that holds the plurality of long pinion gears 38b so as to be rotatable (rotatable) and revolved. The ring gear 37 of the second planetary gear mechanism 35 is connected to the output shaft 27. The planetary carrier 39 is supported by the transmission case 22 via the one-way clutch F1, and the rotation direction of the planetary carrier 39 is limited to one direction by the one-way clutch F1.

  The clutch C1 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 35 The multi-plate friction type hydraulic clutch (friction engagement element) is configured to be able to fasten the first sun gear 36a and release the fastening of both. The clutch C2 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like, and the input shaft 26 and the planetary carrier 39 of the second planetary gear mechanism 35 are fastened. In addition, it is configured as a multi-plate friction type hydraulic clutch that can release the fastening of both. The clutch C3 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 35 This is configured as a multi-plate friction type hydraulic clutch capable of fastening the second sun gear 36b and releasing the fastening of both. The clutch C4 has a hydraulic servo including a piston, a plurality of friction plates and separator plates, an oil chamber to which hydraulic oil is supplied, and the like. The planetary carrier 34 and the second planetary gear mechanism 35 of the first planetary gear mechanism 30 are provided. This is configured as a multi-plate friction hydraulic clutch that can fasten the second sun gear 36b and release the fastening of the two.

  The brake B1 has a hydraulic servo including a plurality of friction plates, separator plates, an oil chamber to which hydraulic oil is supplied, and the like, so that the second sun gear 36b of the second planetary gear mechanism 35 cannot be rotated to the transmission case 22. It is configured as a multi-plate friction type hydraulic brake that can fix and release the fixing of the second sun gear 36b to the transmission case 22. The brake B2 has a hydraulic servo including a plurality of friction plates, separator plates, an oil chamber to which hydraulic oil is supplied, and the planetary carrier 39 of the second planetary gear mechanism 35 is fixed to the transmission case 22 so as not to rotate. At the same time, the planetary carrier 39 is configured as a multi-plate friction type hydraulic brake capable of releasing the fixing to the transmission case 22.

  The one-way clutch F1 has, for example, an inner race, an outer race, a plurality of sprags, and the like, and the planetary carrier 39 rotates forward with respect to the transmission case 22 (the rotation direction of the input shaft 26 and the output shaft 27 during forward traveling is forward rotation). And the planetary carrier 39 can be prevented from rotating in reverse with respect to the transmission case 22.

  The clutches C <b> 1 to C <b> 4 and the brakes B <b> 1 and B <b> 2 of the first transmission 25 operate by receiving and supplying hydraulic oil from the hydraulic control device 60. FIG. 3 is an explanatory diagram showing an operation table showing the relationship between the respective speeds of the first transmission 25 and the operating states of the clutches C1 to C4, the brakes B1, B2, and the one-way clutch F1, and FIG. FIG. 4 is an explanatory diagram illustrating a speed diagram illustrating the relationship between the rotational speeds of rotating elements that constitute one transmission 25; The first transmission 25 sets the first to eighth forward speeds and the first and second reverse speeds by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG. provide. At least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch.

  The second transmission 40 is configured as a two-stage transmission, and in addition to the input shaft 41 connected to the output shaft 27 of the first transmission 25, the second transmission 40 is connected to the drive wheels DW via a differential gear 80. A coupled output shaft 42, a single pinion planetary gear mechanism 45, a dog clutch 50, and a two-way clutch 52 are provided.

  The planetary gear mechanism 45 of the second transmission 40 includes a sun gear 46 that is an external gear, a ring gear 47 that is an internal gear disposed concentrically with the sun gear 46, and a plurality of gears that mesh with the sun gear 46 and the ring gear 47. It has a planetary carrier 49 that holds the pinion gear 48 so as to be rotatable (rotatable) and revolved. The sun gear 46 of the planetary gear mechanism 45 is supported by the transmission case 22 via a two-way clutch 52. The ring gear 47 is connected to the input shaft 41. Further, the planetary carrier 49 is connected to the output shaft 42.

  The dog clutch 50 is configured as a meshing element capable of fastening the ring gear 47 of the planetary gear mechanism 45 and the planetary carrier 49 and releasing the fastening of both. The dog clutch 50 is, for example, connected to one of the ring gear 47 and the planetary carrier 49, and the other of the ring gear 47 and the planetary carrier 49, and is movable in the axial direction. A fixed-side fitting portion and a movable-side fitting portion by one of a hydraulic pressure from the hydraulic control device 60 and an urging force of an elastic body (spring). And the engagement between the two is released by the other of the hydraulic pressure and the urging force of the elastic body. The dog clutch 50 may be driven and controlled by an electric actuator or an electromagnetic actuator.

  The two-way clutch 52 includes, for example, an inner race, an outer race, a plurality of sprags, a switching mechanism, and the like, and the sun gear 46 is rotated forward with respect to the transmission case 22 (the rotation direction of the input shaft 41 and the output shaft 42 during forward travel is rotated forward). And a release state in which reverse rotation is permitted, a reverse rotation restriction state in which forward rotation of the sun gear 46 with respect to the transmission case 22 is permitted and a reverse rotation is restricted, and reverse rotation of the sun gear 46 with respect to the transmission case 22 are permitted. The forward rotation restriction state for restricting forward rotation and the bidirectional restriction state for restricting forward rotation and reverse rotation of the sun gear 46 with respect to the transmission case 22 can be switched. In the embodiment, basically, when the shift lever 95 is in the forward travel position (when the input shaft 41 rotates forward) by the drive control of the switching mechanism by an actuator (not shown), the reverse rotation restriction state is set. When 95 is the reverse travel position (when the input shaft 41 rotates in the reverse direction), the forward rotation restricted state is assumed.

  The dog clutch 50 of the second transmission 40 operates by receiving and supplying hydraulic oil from the hydraulic control device 60. FIG. 5 is an explanatory diagram illustrating a speed diagram illustrating the relationship of the rotational speed during forward travel between the rotating elements constituting the second transmission 40. During forward travel, in the second transmission 40, the two-way clutch 52 is in the reverse rotation restricted state. When the dog clutch 50 is released, the planetary carrier 49 of the planetary gear mechanism 45 is disconnected from the ring gear 47, and the power input to the input shaft 41 (ring gear 47) is reduced in speed and torque as shown in the figure. Is transmitted to the output shaft 42 (planetary carrier 49) (a shift stage on the low vehicle speed side is formed). On the other hand, when the dog clutch 50 is engaged, the planetary carrier 49 and the ring gear 47 of the planetary gear mechanism 45 are connected, and the sun gear 46, the planetary carrier 49, and the ring gear 47 rotate together, and as shown, the input shaft 41 ( The power input to the ring gear 47) is transmitted to the output shaft 42 (planetary carrier 49) while maintaining the rotational speed and torque (forms a shift stage on the high vehicle speed side).

  Although not shown, the parking lock mechanism performs parking lock of the drive wheel DW and release thereof. The parking lock mechanism includes a parking gear attached to the planetary carrier 49 of the planetary gear mechanism 45 of the second transmission 40, and a parking pawl that can be engaged with the parking gear. Therefore, the driving wheel DW is locked by locking the planetary carrier 49 by the engagement of the parking gear and the parking pole.

  Although not shown, the transmission ECU 21 is configured as a microprocessor centered on a CPU, and includes a ROM for storing a processing program, a RAM for temporarily storing data, an input / output port, and a communication port in addition to the CPU. . The shift ECU 21 receives the accelerator position Acc from the accelerator pedal position sensor 92 and the shift position SP from the shift position sensor 96 that detects the position of the shift lever 95, the vehicle speed V from the vehicle speed sensor 98, and the input of the first transmission 25. Rotational speed Nin1 from rotational speed sensor 26a attached to shaft 26, rotational speed Nout1 from rotational speed sensor 27a attached to output shaft 27 of first transmission 25 (input shaft 41 of second transmission 40) The rotational speed Nout2 from the rotational speed sensor 42a attached to the output shaft 42 of the second transmission 40 is input via the input port. A drive control signal to the hydraulic control device 60, a drive control signal to an actuator (not shown) of the two-way clutch 52 of the second transmission 40, and the like are output from the transmission ECU 21 through an output port.

  FIG. 6 is an explanatory diagram showing the reduction ratio of the power transmission device 20 (the first transmission 25 and the second transmission 40). The power transmission device 20 mounted on the automobile 10 according to the embodiment includes the first transmission 25 of the eight-speed transmission type and the second transmission 40 of the two-speed transmission type. In addition, a 16-speed transmission can be configured.

  Next, the operation of the automobile 10 according to the embodiment thus configured, particularly the operation of the first transmission 25 and the second transmission 40 of the power transmission device 20 during forward travel will be described. The first transmission 25 and the second transmission 40 are driven and controlled by the transmission ECU 21. First, during forward travel, the two-way clutch 52 of the second transmission 40 is set in a reverse rotation restriction state that allows the sun gear 46 to rotate forward and restricts reverse rotation. At the time of starting, the first transmission 25 is formed with a low speed side gear stage such as the first speed or the second speed, and the second transmission 40 is released with a dog clutch 50 to form a low vehicle speed side speed stage. To do. By setting the second transmission 40 to a low vehicle speed side shift stage, power transmission can be achieved as compared with a configuration without the second transmission 40 or a configuration with the second transmission but engaging the dog clutch 50 at the start. A larger reduction ratio can be achieved for the entire device 20. As a result, a large torque can be output to the drive wheel DW at the time of start-up or acceleration immediately thereafter, and the start-up performance and acceleration performance can be improved. After the start, the first transmission 25 shifts when a shift condition based on the accelerator opening Acc and the vehicle speed V is satisfied.

  After the start, the dog clutch 50 of the second transmission 40 is released (the second transmission 40 is set to the low vehicle speed side) and the accelerator pedal 91 is depressed while the vehicle is traveling forward. Therefore, when the first transmission 25 does not satisfy the speed change condition, the rotational speed Nout1 of the output shaft 27 of the first transmission 25 (the rotation of the input shaft 41 of the second transmission 40). The number Ni2) decreases. In the embodiment, at this time, at least one other engagement element other than the current engagement element corresponding to the current gear position among the engagement elements (clutch C1 to C4, brakes B1 and B2) of the first transmission 25 at this time. Were slip-engaged. Thereby, the rotation speed Nout1 of the output shaft 27 of the 1st transmission 25 can be reduced more rapidly. Here, in the embodiment, the other engagement element is an engagement element of a shift stage that is one step lower than the current shift stage of the first transmission 25. For example, when the first transmission 25 is in the fourth speed, that is, when the clutches C1 and C4 are currently engaged elements, the clutch C3 is assumed to be another engaging element.

  Since the planetary carrier 49 of the planetary gear mechanism 45 is connected to the drive wheel DW and the two-way clutch 52 is in the reverse rotation restricted state, the rotational speed Nout1 (second transmission) of the output shaft 27 of the first transmission 25 When the rotational speed Ni2 of the input shaft 41 of 40), that is, the rotational speed of the ring gear 47 of the planetary gear mechanism 45 decreases, the rotational speed of the sun gear 46 increases. When the rotational speeds of the sun gear 46, the planetary carrier 49, and the ring gear 47 become substantially the same, the dog clutch 50 is engaged. Thus, the second transmission 40 can be automatically shifted from the low vehicle speed side gear stage to the high vehicle speed side gear stage during forward traveling. Moreover, as described above, at least one other engagement element other than the current engagement element of the first transmission 25 is slip-engaged, so that the rotation speed Nout1 of the output shaft 27 of the first transmission 25 can be made more quickly. Therefore, the second transmission 40 can be shifted more quickly. When the second transmission 40 is set to the high vehicle speed side in this way, the second transmission 40 transmits the power while maintaining the rotational speed and torque from the input shaft 41 to the output shaft 42, so that the power can be efficiently transmitted. Can be transmitted. That is, the fuel efficiency can be improved as compared with the case where the second transmission 40 is set to the low vehicle speed side.

  When the automatic transmission of the second transmission 40 is completed in this way, one of the engaging elements engaged by the first transmission 25 is released, and the first transmission 25 is shifted to the second transmission 40. Return to the same gear as the previous gear, or one gear lower than that. For example, when the first transmission 25 is in the fourth speed before the second transmission 40 is shifted (when the clutches C1 and C4 are the current engagement elements and the clutch C3 is the other engagement element), the clutch C3 is released. Then, the first transmission 25 is returned to the fourth speed, or the clutch C4 is released and the first transmission 25 is set to the third speed. Basically, there is no problem with the former, but as can be seen from FIG. 6, before and after engaging the dog clutch 50 when the shift stage of the first transmission 25 before the shift of the second transmission 40 is 4th or higher. In the case where the first transmission 25 is set to be one step lower, the change in the gear ratio (reduction ratio) of the power transmission device 20 as a whole is smaller than in the case where the same gear is used. Therefore, after the shift of the second transmission 40, when the shift stage of the first transmission 25 before the shift of the second transmission 40 is a shift stage of a predetermined shift stage (for example, 4th speed, 5th speed, etc.) or more, By making the gear position of the first transmission 25 one level lower, it is possible to suppress changes in the gear ratio of the entire power transmission device 20 and to improve the ride comfort for the driver.

  Thereafter, the engagement of the dog clutch 50 (the shift speed on the high vehicle speed side) is maintained for the second transmission 40 until the vehicle stops. As a result, the second transmission 40 can efficiently transmit power until the vehicle stops.

  When the vehicle 10 travels backward, the two-way clutch 52 of the second transmission 40 is set in the forward rotation restricted state, and the output shaft 27 of the first transmission 25 (the input shaft 41 of the second transmission 40) or the second speed change. Except for the point that the output shaft 42 of the machine 40 rotates in the reverse direction, it can be considered in the same way as when traveling forward.

  In the automobile 10 equipped with the power transmission device 20 of the embodiment described above, the planetary gear mechanism 45 in which the ring gear 47 and the planetary carrier 49 are connected to the output shaft 27 of the first transmission 25 and the drive wheel DW, and the ring gear A second clutch 40 having a dog clutch 50 for connecting and releasing 47 and planetary carrier 49, and a two-way clutch 52 interposed between sun gear 46 of planetary gear mechanism 45 and transmission case 22. When traveling forward, the two-way clutch 52 is set in a reverse rotation restricting state in which rotation in the same direction as the ring gear 47 and the planetary carrier 49 of the sun gear 46 is allowed and rotation in the opposite direction is restricted. At the time of starting, when the dog clutch 50 is disengaged, the second transmission 40 is shifted to the low speed side, and when the amount of depression of the accelerator pedal 91 is subsequently reduced, the rotation speed of the ring gear 47 and the sun gear 46 are reduced. The dog clutch 50 is engaged with the increase in the rotational speed, and the second transmission 40 is shifted to the gear position on the high vehicle speed side. Thus, the automatic transmission of the second transmission 40 (shift from the low vehicle speed side gear stage to the high vehicle speed side gear stage) can be performed during traveling. In addition, when starting off, acceleration can be improved at the low speed side gear stage, and after engagement of the dog clutch 50, fuel efficiency can be improved at the high speed side gear stage.

  In the automobile 10 of the embodiment, after the dog clutch 50 is engaged, the engagement of the dog clutch 50 is maintained until the vehicle stops. As a result, the second transmission 40 can efficiently transmit power until the vehicle stops.

  In the automobile 10 of the embodiment, when the amount of depression of the accelerator pedal 91 is reduced while the dog clutch 50 is disengaged (the second transmission 40 is set to the low speed side gear) and the vehicle is traveling forward, the first shift is performed. The rotation speed Nout1 of the output shaft 27 of the machine 25 (the rotation speed Ni2 of the input shaft 41 of the second transmission 40) is reduced and the dog clutch 50 is engaged. The dog clutch 50 may not be engaged at the following speeds (for example, the second speed or the third speed). In this way, the second transmission 40 can be driven at a low vehicle speed regardless of whether or not the amount of depression of the accelerator pedal 91 has decreased until the gear position of the first transmission 25 becomes higher than the predetermined gear position after starting. It is held at the shift stage on the side. Accordingly, it is possible to further increase the time from the start until the second transmission 40 is shifted to the gear position on the high vehicle speed side.

  Here, when the dog clutch 50 is not engaged when the amount of depression of the accelerator pedal 91 is decreased (the second transmission 40 is not shifted), the rotational speed Nout1 of the output shaft 27 of the first transmission 25 is rapidly reduced. Since it is not necessary, it is not necessary to slip-engage at least one other engagement element of the first transmission 25.

  Further, when the dog clutch 50 is not engaged when the depression amount of the accelerator pedal 91 is decreased, the two-way clutch 52 may be set in a bidirectional restricted state (a state in which the forward rotation and the reverse rotation of the sun gear 46 are restricted). By so doing, it is possible to restrict the sun gear 46 from rotating forward (approaching the rotational speed of the ring gear 47), so that the engine brake can be applied to the drive wheels DW.

  In the vehicle 10 of the embodiment, when the amount of depression of the accelerator pedal 91 is reduced while the dog clutch 50 is released (the second transmission 40 is set to a low vehicle speed side gear) and the vehicle is traveling forward, the first transmission As the at least one other engagement element other than the current engagement element 25, an engagement element of a gear position that is one step lower than the current gear position of the first transmission (for example, when the first transmission 25 is in the fourth speed, that is, When the clutches C1 and C4 are currently engaging elements, the clutch C3) is slip-engaged, but engaging elements other than the engaging element of the gear stage that is one step lower may be slip-engaged.

  In the vehicle 10 of the embodiment, when the amount of depression of the accelerator pedal 91 is reduced while the dog clutch 50 is released (the second transmission 40 is set to a low vehicle speed side gear) and the vehicle is traveling forward, the second transmission In order to automatically shift the gear 40, at least one other engagement element other than the current engagement element of the first transmission 25 is slip-engaged, whereby the rotation speed Nout1 of the output shaft 27 of the first transmission 25 (second Although the rotational speed Ni2) of the input shaft 41 of the transmission 40 is decreased, the torque of the engine 12 may be decreased from a value corresponding to the accelerator opening Acc in addition to or instead of this. In this case, the rotational speed Nout1 of the output shaft 27 of the first transmission 25 can be reduced more quickly due to the reduction in the torque of the engine 12. Further, when the amount of depression of the accelerator pedal 91 is reduced while the dog clutch 50 is released and the vehicle is traveling forward, at least one other engagement element of the first transmission 25 is slip-engaged, or the engine 12 The torque may not be reduced below a value corresponding to the accelerator opening Acc. In this case, the rotational speed of the output shaft 27 of the first transmission 25 (the rotational speed of the ring gear 47) decreases due to the decrease in the torque of the engine 12 according to the decrease in the depression amount of the accelerator pedal 91, and the rotational speed of the planetary carrier 49. The dog clutch 50 is engaged. For this reason, although the time until the rotational speed of the ring gear 47 becomes substantially the same as the rotational speed of the planetary carrier 49 is slightly increased, the second transmission 40 can be shifted.

  In the power transmission device 20 of the automobile 10 according to the embodiment, the second transmission 40 includes the planetary gear mechanism 45, the dog clutch 50, and the two-way clutch 52, but the power transmission device 120 according to the modification of FIG. As described above, the second transmission 140 may include the planetary gear mechanism 45, the dog clutch 50, the one-way clutch 152, and the dog brake 153 as a meshing brake. Here, the one-way clutch 152 and the dog brake 153 are arranged such that the dog brake 153 is interposed between the one-way clutch 152 and the transmission case 22. The one-way clutch 152 allows forward rotation of the sun gear 46 with respect to the transmission case 22 and restricts reverse rotation when the dog brake 153 is engaged (functions similarly to the reverse rotation restricted state of the two-way clutch 52 of the embodiment). Configured). In this case, during forward travel, by engaging the dog brake 153, the one-way clutch 152 functions in the same manner as the two-way clutch 52 of the embodiment, so that the second transmission 40 is automatically shifted during travel as in the embodiment. can do. On the other hand, during reverse travel, the dog brake 153 is released, the dog clutch 50 is engaged, and the sun gear 46, the planetary carrier 49, and the ring gear 47 are rotated together, so that the reverse travel is performed as in the configuration without the second transmission 40. You can travel.

  In the power transmission device 20 of the automobile 10 of the embodiment and the power transmission device 120 of the modified example, the dog clutch 50 of the second transmission 40 fastens the ring gear 47 of the planetary gear mechanism 45 and the planetary carrier 49 and fastens them. However, since it is sufficient that the sun gear 46, the planetary carrier 49, and the ring gear 47 can be integrally rotated and released, the sun gear 46 and the planetary carrier 49 may be fastened and the fastening of both may be released. The sun gear 46 and the ring gear 47 may be fastened and the fastening of both may be released.

  In the power transmission device 20 of the vehicle 10 according to the embodiment, the second transmission 40 includes the planetary gear mechanism 45, the dog clutch 50, and the two-way clutch 52. However, the power transmission device 220 illustrated in FIG. As described above, the second transmission 240 may include the planetary gear mechanism 45, the dog clutch 250, and the one-way clutch 152. Here, like the one-way clutch 152, the one-way clutch 252 allows forward rotation of the sun gear 46 with respect to the transmission case 22 and restricts reverse rotation (functions similarly to the reverse-rotation restricted state of the two-way clutch 52 of the embodiment). ) Is configured as follows. The dog clutch 250 includes a first gear 250 a connected to the sun gear 46 of the planetary gear mechanism 45, a second gear 250 b connected to the ring gear 47 of the planetary gear mechanism 45, and a third gear 250 c connected to the transmission case 22. And a movable member 250d that can move in the axial direction (left-right direction in the figure) of the planetary gear mechanism 45 and the output shaft 42. The first, second, and third gears 250a, 250b, and 250c are arranged at predetermined intervals in the axial direction. The movable member 250d is formed so as to be able to mesh with the first, second, and third gears 250a, 250b, and 250c. By moving the movable member 250 d in the axial direction, the sun gear 46 of the planetary gear mechanism 25 is connected to the ring gear 47 and the transmission case 22, and the sun gear 46 of the planetary gear mechanism 45 is connected to the ring gear 47. The second state (where the sun gear 46, the planetary carrier 49, and the ring gear 47 are integrally rotated) and the third state where the sun gear 46 is fixed (connected) to the transmission case 22 so as not to rotate can be switched. FIG. 9 is an explanatory diagram illustrating a speed diagram illustrating the relationship between the rotational speeds of the rotating elements constituting the second transmission 240. During forward travel, the second transmission 240 sets the dog clutch 250 to the first state and the second state, so that the second transmission 240 has a low vehicle speed side and a high vehicle speed side for forward travel as in the second transmission 40 of the embodiment. A gear position (see “Dlo” and “Dhi” in the figure) can be formed. During reverse travel, the dog clutch 250 is set to the third state, so that the sun gear 46 is fixed to the transmission case 22 to form a reverse gear (see “Rev” in the figure). it can.

  In the power transmission device 220 of this modification, the dog clutch 250 is configured so that the sun gear 46 of the planetary gear mechanism 45 can be connected to the ring gear 47, but the sun gear 46 of the planetary gear mechanism 45 can be connected to the planetary carrier 49. It is good also as what is comprised by.

  In the automobile 10 of the embodiment, the planetary gear mechanism 45 of the second transmission 40 is configured as a single pinion planetary gear, but may be configured as a double pinion planetary gear.

  The automobile 10 according to the embodiment includes the first transmission 30 of the eight-speed transmission type, but is not limited to the eight-speed transmission system, and is a four-speed transmission system, a five-speed transmission system, or a six-speed transmission system. Any number of transmissions such as a formula may be provided.

  In the automobile 10 of the embodiment, the parking lock mechanism is arranged so that the rotation of the planetary carrier 49 of the planetary gear mechanism 45 of the second transmission 40 can be locked and released. When the dog clutch 50 is engaged at the time of parking, the rotation of the rotation shaft (for example, the output shaft 27) of the first transmission 25 may be locked and released.

  The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. In the embodiment, the first transmission 25 having the first planetary gear mechanism 30, the second planetary gear mechanism 35, the clutches C1 to C4, the brakes B1 and B2, and the one-way clutch F1 corresponds to a “first transmission”. The second transmission 40 having the planetary gear mechanism 45, the dog clutch 50, and the two-way clutch 52 corresponds to a “second transmission”, and the transmission ECU 21 corresponds to a “control unit”.

  The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is the same as that of the embodiment described in the column of means for solving the problem. Therefore, the elements of the invention described in the column of means for solving the problems are not limited. That is, the interpretation of the invention described in the column of means for solving the problems should be made based on the description of the column, and the examples are those of the invention described in the column of means for solving the problems. It is only a specific example.

  As mentioned above, although the form for implementing this invention was demonstrated using the Example, this invention is not limited at all to such an Example, In the range which does not deviate from the summary of this invention, it is with various forms. Of course, it can be implemented.

  The present invention can be used in the power transmission device manufacturing industry.

  DESCRIPTION OF SYMBOLS 10 Car, 12 Engine, 13 Crankshaft, 14 Engine electronic control unit (engine ECU), 15 Brake electronic control unit (brake ECU), 20, 120, 220 Power transmission device, 21 Shift electronic control unit (shift ECU) ), 22 transmission case, 23 starter, 23c lock-up clutch, 23d damper mechanism, 23o one-way clutch, 23p pump impeller, 23s stator, 23t turbine runner, 24 oil pump, 25 first transmission, 26 input shaft, 26a rotation Number sensor, 27 output shaft, 27a rotational speed sensor, 30 first planetary gear mechanism, 31 sun gear, 32 ring gear, 33a, 33b pinion gear, 34 planetary carrier, 35 second planetary gear mechanism, 36a 1st sun gear, 36b 2nd sun gear, 37 ring gear, 38a short pinion gear, 38b long pinion gear, 39 planetary carrier, 40, 140, 240 2nd transmission, 41 input shaft, 42 output shaft, 42a rotational speed sensor, 45 planetary gear Mechanism, 46 Sun gear, 47 Ring gear, 48 Pinion gear, 49 Planetary carrier, 50 Dog clutch, 52 Two-way clutch, 60 Hydraulic control device, 80 Differential gear, 91 Accelerator pedal, 92 Accelerator pedal position sensor, 93 Brake pedal, 94 Master cylinder pressure sensor , 95 shift lever, 96 shift position sensor, 98 vehicle speed sensor, 152 one-way clutch, 153 dog brake, 250 dog clutch, 250a Gear, 250b a second gear, 250c third gear, 250d movable member, 252 one-way clutch, B1, B2 brake, C1, C2, C3, C4 clutch, DW drive wheels, F1 the one-way clutch.

Claims (7)

A power transmission device mounted on a vehicle and transmitting power from a prime mover to an axle,
A stepped first transmission connected to the output shaft of the prime mover;
A two-stage second transmission connected to the output shaft of the first transmission and the axle;
Control means for controlling the first transmission and the second transmission;
With
The second transmission includes a planetary gear mechanism having a first rotation element connected to an output shaft of the first transmission, a second rotation element connected to the axle, and a third rotation element; A meshing clutch that connects and disconnects two of the rotating element, the second rotating element, and the third rotating element, and at least the first direction in a direction opposite to the rotating direction of the first rotating element during forward traveling. A rotation restricting means capable of restricting the rotation of the three-rotating element, and a gear position on the low vehicle speed side is formed by releasing the meshing clutch, and a gear stage on the high vehicle speed side is formed by engaging the meshing clutch. Configured,
The control means engages the meshing clutch when the accelerator depression amount is reduced during traveling forward with the meshing clutch being released.
Power transmission device. The power transmission device according to claim 1,
The control means holds the engagement of the engagement clutch until the vehicle stops after engaging the engagement clutch.
Power transmission device. The power transmission device according to claim 1 or 2,
When the accelerator depression amount is reduced during the forward running while releasing the mesh clutch, the control means decreases the rotation speed of the first rotation element and increases the rotation speed of the third rotation element. And when the first rotating element, the second rotating element, and the third rotating element have substantially the same number of rotations, the meshing clutch is engaged.
Power transmission device. The power transmission device according to any one of claims 1 to 3,
The rotation restricting means is capable of restricting bidirectional rotation of the third rotating element.
Power transmission device. The power transmission device according to any one of claims 1 to 4,
The rotation restricting means is configured as a two-way clutch capable of restricting the rotation of the third rotating element in a direction opposite to the rotating direction of the first rotating element according to a shift position.
The control means engages the meshing clutch when the accelerator depression amount is reduced while the meshing clutch is released and traveling forward or backward.
Power transmission device. The power transmission device according to any one of claims 1 to 4,
The rotation restricting means houses a one-way clutch that restricts the rotation of the third rotating element in a direction opposite to the rotating direction of the first rotating element during forward travel, and a case that houses the one-way clutch and the second transmission. A second meshing clutch interposed between
The control means engages the meshing clutch and releases the second meshing clutch during reverse travel.
Power transmission device. The power transmission device according to any one of claims 1 to 3,
The rotation restricting means has a one-way clutch that restricts the rotation of the third rotating element in the direction opposite to the rotating direction of the first rotating element during forward traveling,
The meshing clutch includes a first state in which the third rotating element is not connected to the first rotating element or the second rotating element or a case housing the second transmission, and the third rotating element is connected to the first rotating element. It is configured to be switchable between a second state in which it is connected to one rotation element or the second rotation element and a third state in which the third rotation element is non-rotatably connected to the case,
The second transmission forms a low speed side gear for forward travel by setting the meshing clutch to the first state, and sets the meshing clutch for the forward travel by setting the meshing clutch to the second state. A speed stage for vehicle travel is formed, and a gear stage for reverse travel is formed by setting the meshing clutch to the third state.
Power transmission device.

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