JP2010173395A - Multi-stage automatic transmission for hybrid vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To achieve multi-stage automatic speed change with a simple structure, wherein a skeleton of an existing automatic transmission is used to constitute it, in a multi-stage automatic transmission for a hybrid vehicle in which an intermediate member for connecting: a transmission constituted by a plurality of planetary mechanisms; and a starting clutch, is rotatably controlled by a motor generator. <P>SOLUTION: The transmission M is constituted by: a speed increasing planetary mechanism PI; and a speed changing planetary mechanism PC for speed changing a drive force inputted from the speed increasing planetary mechanism PI to a predetermined shift stage and transmitting it to an output member 14 side. A first element LSc fixable to the ground by a first brake B1 is disengageably connected to the intermediate member 11 through a first clutch C1, and a second element Cc fixable to the ground by a second brake B2 is disengageably connected to the speed increasing planetary mechanism PI through a second clutch C2. A third element SSc is connected to the intermediate member 11 through a third clutch C3 and a fourth element Rc is connected to an output member 14. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention rotatably controls a transmission including a plurality of planetary mechanisms, a starting clutch capable of transmitting driving force from an engine to the transmission, and an intermediate member connecting the starting clutch and the transmission. The present invention relates to a multi-stage automatic transmission for a hybrid vehicle including a motor / generator.

  Such a multi-stage automatic transmission for a hybrid vehicle is known from Patent Document 1.

Japanese translation of PCT publication No. 2005-500481

  By the way, what is disclosed in the above-mentioned Patent Document 1 enables automatic forward shifting of six forward speeds and one reverse speed, but requires five clutches and three brakes, has many components, and has a structure. Is complicated.

  The present invention has been made in view of such circumstances, and has a simple structure that can be configured by diverting the framework of an existing automatic transmission, and a multi-stage of a hybrid type vehicle that enables multi-stage automatic transmission. An object is to provide an automatic transmission.

  In order to achieve the above object, the invention according to claim 1 is a transmission comprising a plurality of planetary mechanisms, a starting clutch capable of transmitting driving force from an engine to the transmission, the starting clutch and the In a multi-stage automatic transmission for a hybrid vehicle including a motor / generator that rotatably controls an intermediate member that connects the transmission, the transmission includes a speed increasing planetary mechanism that increases a driving force directly input from the engine; And a transmission planetary mechanism that has a first to a fourth element and that transmits a driving force input from the speed-up planetary mechanism to the output member at a predetermined shift speed, and is fixed to the ground by a first brake. A possible first element is detachably connected to the intermediate member via a first clutch, and a second element that can be fixed to the ground by a second brake is the speed increasing member. Via the second clutch is engaged detachably connected to Ranetari mechanism, the third element is connected through a third clutch to said intermediate member, the fourth element is characterized in that it is connected to the output member.

  According to a second aspect of the invention, in addition to the configuration of the first aspect of the invention, the transmission planetary mechanism includes a large sun gear as a first element, a carrier as a second element, a small sun gear as a third element, and a fourth element. As a ring gear, it is configured as a Ravigneaux type.

  Furthermore, the invention according to claim 3 is characterized in that, in addition to the configuration of the invention according to claim 2, power from the speed-up planetary mechanism is input to the carrier via a second clutch.

  The output gear 14 of the embodiment corresponds to the output member of the present invention.

  According to the first to third aspects of the present invention, the speed-up planetary mechanism and the speed-change planetary mechanism that transmits the driving force input from the speed-up planetary mechanism to the output gear while shifting the speed to a predetermined gear stage. In addition to the transmission, the multi-stage transmission can be realized with a simple structure with a reduced number of parts including the start clutch, the first to third clutches, and the first and second brakes.

It is a skeleton figure which shows a multistage automatic transmission typically. It is a speed diagram at the time of performing multi-stage speed change operation, performing motor assist and energy regeneration. FIG. 5 is a velocity diagram when performing multi-stage speed change operation only with the output of a motor / generator. It is a speed diagram at the time of performing continuously variable transmission by making the 2nd and 3rd clutch into a power transmission state. It is a speed diagram at the time of performing continuously variable transmission by making the 1st and 2nd clutch into a power transmission state.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  A first embodiment of the present invention will be described with reference to FIGS. 1 to 5. First, in FIG. 1, the multi-stage automatic transmission includes a speed increasing planetary mechanism PI and a Ravigneaux type speed changing planetary mechanism PC. M, a starting clutch CS capable of transmitting the driving force from the engine E to the transmission M, an intermediate member 11 connecting the starting clutch CS and the transmission M, and the intermediate member portion 11 are rotatably controlled. Motor generator M / G.

  The crankshaft 12 of the engine E is connected to an input shaft 13 coaxial with the crankshaft 12 via a damper DP, and the start clutch CS is interposed between the intermediate member 11 and the input shaft 13.

  The speed-up planetary mechanism PI speeds up the power input from the input shaft 13 and transmits the speed to the speed-change planetary mechanism PC, and includes a sun gear Si fixed to the transmission case 15 and the input shaft. A first carrier Ci that rotates together with the first carrier Ci, a first pinion 16 that is rotatably supported by the first carrier Ci and meshes with the sun gear Si, and a first ring gear Ri that meshes with the first pinion 16. Configured.

  The transmission planetary mechanism PC has a large sun gear LSc as a first element, a second carrier Cc as a second element, a small sun gear SSc as a third element, and a second ring gear Rc as a fourth element. The driving force input from the speed-up planetary mechanism PI is shifted to a predetermined gear position and transmitted to the output gear 14 as an output member.

  The large sun gear LSc is disposed coaxially with the input shaft 13 and is detachably coupled to the intermediate member 11 via a first clutch C1, and the second carrier Cc is a first of the acceleration planetary mechanism PI. The ring gear Ri is detachably connected via the second clutch C2, the small sun gear SSc is detachably connected to the intermediate member 11 via the third clutch C3, and the second ring gear Rc is an output member. Connected to the gear 14.

  A second pinion 17 meshing with the small sun gear SSc and a third pinion 18 meshing with the second pinion 17 and the second ring gear Rc are rotatably supported on the second carrier Cc, and the third pinion 18 is a large sun gear. Also meshes with LSC.

  A first brake B1 is provided between the large sun gear LSc of the transmission planetary mechanism PC and the transmission case 15, and the large sun gear LSc can be fixed to the ground by the first brake B1. A second brake B2 is provided between the second carrier Cc of the transmission planetary mechanism PC and the transmission case 15, and the second carrier Cc can be fixed to the ground by the second brake B2.

  In such a multi-stage automatic transmission, the friction engagement state (●) of the starting clutch CS, the first to third clutches C1, C2, C3, and the first and second brakes B1, B2 is set as shown in Table 1. As a result, the motor can be driven by switching between the seven forward shift stages and the one reverse stage while performing motor assist by the output of the motor / generator M / G and energy regeneration by the motor / generator M / G. The power from the engine E is transmitted as shown by the solid arrow in FIG. 2, and the power from the motor / generator M / G and the power input to the motor / generator M / G at the time of regeneration are indicated by the chain arrows in FIG. Indicated.

  Here, the left part of FIG. 2 shows the speed increasing planetary mechanism PI, and the right part shows the speed changing planetary mechanism PC, and the lower horizontal solid line on the speed changing planetary mechanism PC side indicates the speed “0”. The second horizontal solid line from the bottom on the mechanism PC side indicates the rotational speed inputted to the large sun gear LSc or the small sun gear SSc, and the horizontal broken line arranged above the second horizontal solid line is from the acceleration planetary mechanism PI. The rotational speed input into the speed planetary mechanism PC is shown. Also, the vertical lines in FIG. 2 indicate the sun gear Si of the speed increasing planetary mechanism PI, the first carrier Ci and the first ring gear Ri, the large sun gear LSc of the speed changing planetary mechanism PC, the second carrier Cc, and the second ring gear Rc in order from the right side. And a small sun gear SSc.

  Thus, in the reverse speed, the second and third clutches C2 and C3 are in the power cut-off state, the first brake B1 is in the non-braking state, the start clutch CS and the first clutch C1 are in the power transmission state, and the second By setting the brake B2 to the braking state, the increased power is not transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC. In the speed-change planetary mechanism PC, the second carrier Cc is stationary and small. The sun gear SSc can idle around the axis of the input shaft 13, and the power from the engine E and the motor / generator M / G is transmitted to the large sun gear LSc.

  At the first forward speed, the first and second clutches C1 and C2 are in a power cut-off state, the first brake B1 is in a non-braking state, the start clutch CS and the third clutch C3 are in a power transmission state, By setting the second brake B2 to the braking state, the increased power is not transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC, and the second carrier Cc is fixed to the ground in the speed-change planetary mechanism PC. At the same time, the large sun gear LSc can idle around the input shaft 13, and the power from the engine E and the motor / generator M / G is transmitted to the small sun gear SSc.

  At the second forward speed, the first and second clutches C1 and C2 are in a power cut-off state, the second brake B2 is in a non-braking state, the start clutch CS and the third clutch C3 are in a power transmission state, By setting one brake B1 to the braking state, the increased power is not transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC side. In the speed-change planetary mechanism PC, the second carrier Cc is input to the input shaft 13. The large sun gear LSc is fixed to the ground, and the power from the engine E and the motor / generator M / G is transmitted to the small sun gear SSc.

  At the third forward speed, the second clutch C2 is in the power cut-off state and the first and second brakes B1, B2 are in the non-braking state, and the starting clutch CS, the first clutch C1, and the third clutch C3 are powered. By setting the transmission state, the speed-increased power is not transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC. In the speed-change planetary mechanism PC, the second carrier Cc is moved around the axis of the input shaft 13. It can idle, and the power from the engine E and the motor / generator M / G is transmitted to the large sun gear LSc and the small sun gear SSc.

  At the fourth forward speed, the first clutch C1 is in the power cut-off state and the first and second brakes B1 and B2 are in the non-braking state, and the starting clutch CS, the second clutch C2, and the third clutch C3 are powered. By setting the transmission state, the increased power is transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC. In the speed-change planetary mechanism PC, the second carrier Cc is transmitted to the speed-up planetary mechanism PI. The large sun gear LSc rotates with the one ring gear Ri and can idle around the input shaft 13, and the power from the engine E and the motor / generator M / G is transmitted to the small sun gear SSc.

  At the fifth forward speed, the start clutch CS is in a power cut-off state, the first and second brakes B1 and B2 are in a non-braking state, and the first to third clutches C1 to C3 are in a power transmission state. Is transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC. In the speed-change planetary mechanism PC, the second carrier Cc rotates together with the first ring gear Ri of the speed-up planetary mechanism PI, and the large sun gear. Power from engine E and motor / generator M / G is transmitted to LSc and small sun gear SSc.

  At the sixth forward speed, the third clutch C3 is in the power cut-off state and the first and second brakes B1 and B2 are in the non-braking state, and the starting clutch CS, the second clutch C2, and the second clutch C2 are powered. By setting the transmission state, the increased power is transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC. In the speed-change planetary mechanism PC, the second carrier Cc is combined with the first ring gear Ri of the speed-up planetary mechanism PI. The small sun gear SSc rotates idly around the input shaft 13, and the power from the engine E and the motor / generator M / G is transmitted to the large sun gear LSc.

  At the seventh forward speed, the first and third clutches C1 and C3 are in a power cut-off state, the second brake B2 is in a non-braking state, and the start clutch CS and the second clutch C2 are in a power transmission state. By setting the first brake B1 to the braking state, the increased power is transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC, and in the speed-change planetary mechanism PC, the second carrier Cc is transmitted to the speed-up planetary mechanism PI. It rotates together with the first ring gear Ri, the large sun gear LSc is fixed to the ground, and the small large sun gear LSc can idle around the input shaft 13.

  Further, by setting the friction engagement state (●) of the starting clutch CS, the first to third clutches C1 to C3, and the first and second brakes B1 and B2 as shown in Table 2, three forward shift speeds Further, the vehicle can be driven only by the output of the motor / generator M / G by switching the reverse stage of one stage, and the speed characteristic at this time is as shown in FIG.

  At this time, in the reverse speed, the starting clutch CS, the second clutch C2, and the third clutch C3 are set in the power cut-off state, the first brake B1 is set in the non-braking state, the first clutch C1 is set in the power transmission state, and the second By setting the brake B2 to the braking state, the increased speed power is not transmitted from the speed increasing planetary mechanism PI to the speed changing planetary mechanism PC, and the second carrier Cc is fixed to the ground in the speed changing planetary mechanism PC. At the same time, the large sun gear LSc can idle around the axis of the input shaft 13, and the power from the motor / generator M / G is transmitted to the small sun gear SSc.

  At the first forward speed, the starting clutch CS, the first clutch C1, and the second clutch C2 are in the power cut-off state, the first brake B1 is in the non-braking state, and the third clutch C3 is in the power transmission state. At the same time, the second brake B2 is brought into the braking state, so that the increased power is not transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC, and the second carrier Cc is grounded in the speed-change planetary mechanism PC. While being fixed, the small sun gear SSc can idle around the axis of the input shaft 13, and the power from the motor / generator M / G is transmitted to the large sun gear LSc.

  At the second forward speed, the starting clutch CS, the first clutch C1, and the second clutch C2 are in a power cut-off state, the second brake B2 is in a non-braking state, and the third clutch C3 is in a power transmission state. By setting the first brake B1 to the braking state, the increased power is not transmitted from the speed increasing planetary mechanism PI to the speed changing planetary mechanism PC side. In the speed changing planetary mechanism PC, the second carrier Cc is input to the input shaft. The large sun gear LSc can idle around the input shaft 13, and the power from the motor / generator M / G is transmitted to the small sun gear SSc.

  Further, at the third forward speed, the starting clutch CS and the second clutch C2 are set in the power cut-off state, the first and second brakes B1 and B2 are set in the non-braking state, and the first and third clutches C1 and C3 are set in the non-braking state. By setting the power transmission state, the speed-increased power is not transmitted from the speed-up planetary mechanism PI to the speed-change planetary mechanism PC. In the speed-change planetary mechanism PC, the second carrier Cc is rotated around the axis of the input shaft 13. The power from the motor / generator M / G is transmitted to the large sun gear LSc and the small sun gear SSc.

  Further, by setting the friction engagement state (●) of the starting clutch CS, the first to third clutches C1 to C3, and the first and second brakes B1 and B2 as shown in Table 3, the motor generator M / G In this case, the vehicle can be run while continuously changing the speed, and the speed characteristic diagram when the second and third clutches C2 and C3 are in the power transmission state is as shown in FIG. FIG. 5 shows a speed characteristic diagram when the first and second clutches C1 and C2 are in a power transmission state.

  Thus, the continuously variable speed travel when the second and third clutches C2 and C3 are in the power transmission state is the fourth speed when the vehicle is traveled by switching between the seven forward speeds and the reverse speed. The first and second clutches C1 and C2 are in a power transmission state, and can be continuously variable by changing the output rotation speed of the motor / generator M / G. The continuously variable speed travel corresponds to the sixth forward shift speed when the vehicle is driven by switching between the seven forward shift speeds and the first reverse speed, and the motor / generator M / It is possible to perform continuously variable transmission by changing the output rotation speed of G.

  Next, the operation of the first embodiment will be explained. The transmission M shifts and transmits the speed increasing planetary mechanism PI and the driving force input from the speed increasing planetary mechanism PI to the output gear 14 side at a predetermined speed. The large sun gear LSc of the transmission planetary mechanism PC can be fixed to the ground by the first brake B1 and is detachably connected to the intermediate member 11 via the first clutch C1. The second carrier Cc of the speed-change planetary mechanism PC can be fixed to the ground by the second brake B2, and is detachably connected to the first ring gear Ri of the speed-up planetary mechanism PI via the second clutch C2, so that the speed-change planetary mechanism PC. The small sun gear SSc is connected to the intermediate member 11 via the third clutch C3, and the transmission planetary mechanism PC The two-ring gear Rc is simply configured to be connected to the output gear 14, and in addition to the transmission M, the starting clutch CS, the first to third clutches C1 to C3, and the first and second brakes B1 and B2 are provided. With a simple structure with only a small number of parts included, it is possible to realize a multi-speed shift with 7 forward speeds and 1 reverse speed.

  Moreover, when the portion surrounded by the dotted line in FIG. 1, that is, the portion including the motor / generator M / G, the intermediate member 11 and the damper DP is converted into a torque converter, an automatic transmission with a torque converter is obtained. It is possible to make use of this skeleton.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the present invention described in the claims. Is possible.

11 ... intermediate member 14 ... output gear B1 as output member ... first brake B2 ... second brake C1 ... first clutch C2 ... second clutch C3 ... third Clutch Cc ... Carrier CS as the second element ... Starting clutch E ... Engine LSc ... Large sun gear M as the first element ... Transmission M / G ... Motor generator PC ..Transmission planetary mechanism PI ... Speed increasing planetary mechanism Rc ... Ring gear SSc as the fourth element ... Small sun gear as the third element

Claims (3)

  A transmission (M) composed of a plurality of planetary mechanisms (PI, PC), a starting clutch (CS) capable of transmitting driving force from the engine (E) to the transmission (M), and the starting clutch ( CS) and a motor / generator (M / G) that rotatably controls an intermediate member (11) that connects the transmission (M). In the multistage automatic transmission of a hybrid vehicle, the transmission (M) includes: The speed increasing planetary mechanism (PI) includes a speed increasing planetary mechanism (PI) for increasing the driving force directly input from the engine (E) and first to fourth elements (LSc, Cc, SSc, Rc). The first element that is fixed to the ground by the first brake (B1) is configured with a transmission planetary mechanism (PC) that shifts and transmits the driving force input from the transmission member to the output member (14) to a predetermined gear position. ( Sc) is detachably connected to the intermediate member (11) via the first clutch (C1), and the second element (Cc) that can be fixed to the ground by the second brake (B2) is the speed-up planetary mechanism ( PI) is detachably connected via a second clutch (C2), a third element (SSc) is connected to the intermediate member (11) via a third clutch (C3), and a fourth element (Rc ) Is coupled to the output member (14). A multi-stage automatic transmission for a hybrid vehicle.   The transmission planetary mechanism (PC) is configured in a Ravigneaux type with a first element as a large sun gear (LSc), a second element as a carrier (Cc), a third element as a small sun gear (SSc), and a fourth element as a ring gear (Rc). The multi-stage automatic transmission for a hybrid vehicle according to claim 1, wherein   The multistage automatic transmission for a hybrid vehicle according to claim 2, wherein power from the speed increasing planetary mechanism (PI) is input to the carrier (Cc) via a second clutch (C2).

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