Control system for drive unit of hybrid vehicle

This invention relates to a control system for a drive unit of a hybrid vehicle having an electric motor and another power unit as prime movers, and in which powers from the prime movers are outputted through a transmission.

In the prior art, for example, there is known a drive unit for a hybrid vehicle, in which power of an internal combustion engine is distributed to an output member and to a motor generator through a planetary gear mechanism, in which the motor generator is used as a reaction member, and in which a revolution frequency of the engine is set to achieve a preferable fuel economy in accordance with a revolution frequency of the motor generator. According to this kind of drive unit, an engine revolution and an output torque can be controlled by the motor generator, therefore, the planetary gear mechanism and the motor generator function substantially as a transmission. Here, since the motor generator functions as a generator and establishes reaction force when the engine is outputting power, an electric power generated by the motor generator is supplied to an electric motor connected with the output member, and the power outputted from the electric motor is applied to the output member.

However, according to the drive unit thus configured, a large capacity electric motor applying power to the output member is required in order to obtain large drive force while operating the engine under the condition where the fuel economy is optimum. For this purpose, a drive unit for a hybrid vehicle disclosed in Japanese Patent Laid-Open No. 2003-127681 is adapted to suppress an increase in size of an electric motor, and to obtain driving force in accordance with a various vehicle speeds. Specifically, according to the invention disclosed in Japanese Patent Laid-Open No. 2003-127681, an internal combustion engine is connected with a carrier of a planetary gear mechanism, a first electric motor/generator is connected with a sun gear of the planetary gear mechanism, and a member of an input side of a transmission is connected with a ring gear. A member of an output side of the transmission is connected with a propeller shaft, and a second electric motor/generator is connected with the propeller shaft.

According to the drive unit disclosed in Japanese Patent Laid-Open No. 2003-127681, gear stage regions of the transmission are set in accordance with a vehicle speed, a gear stage corresponding to the gear stage region to which the running condition belong is set by the transmission, and the engine revolution is controlled by the first electric motor/generator to optimize the fuel economy. For this purpose, the second electric motor/generator is arranged upstream of the transmission, and the gear stage of the transmission is basically set in accordance with the vehicle speed even in case a vehicle is run by the power of the second electric motor/generator. Therefore, if the vehicle speed is changed when the vehicle is run by the motor, an upshifting or a downshifting of the transmission is carried out in response to the change in the vehicle speed. However, in case of such a “motor running”, a rotation of the motor is smoother than that of the engine so that noise of the motor resulting from the rotation thereof is also smaller than that of the engine. This means that the fluctuation of the drive force and the noise resulting from a speed change operation of the transmission under the “motor running” are much conspicuous in comparison with those under an “engine running”. Especially, if the “motor running” can be selected by an operation of a switch, a driver or a passenger may feel a running condition different from an intended running condition. That is, a driver or a passenger may feel uncomfortable feeling.

The present invention has been conceived noting the technical problems thus far described, and its object is to provide a control system for a drive unit of a hybrid vehicle, which is capable of reducing a frequency of a speed change operation and alleviating shocks when a vehicle is driven by a power of an electric motor.

In order to achieve the above-mentioned object, according to the present invention, there is provided a control system for a drive unit of a hybrid vehicle having an electric motor, an another power unit other than the electric motor, and a transmission, characterized by comprising: a speed change inhibiting means for inhibiting a speed change operation of the transmission in case a vehicle is run by a power of the electric motor.

According to another aspect of the present invention, there is provided a control system for a drive unit of a hybrid vehicle having an electric motor, an another power unit other than the electric motor, and a transmission, characterized by comprising: a speed change restricting means for restricting a speed change operation of the transmission in case a vehicle is run by a power of the electric motor.

The above-mentioned speed change inhibiting means and speed change restricting means include a means for fixing a speed change ratio of the transmission to a speed change ratio of the lowest speed side.

According to the control system for a drive unit of a hybrid vehicle of the invention, the transmission comprises a unidirectional engagement device which is engaged when setting the speed change ratio of the lowest side under driving state; and a bidirectional engagement device which is arranged in parallel with the unidirectional engagement device.

The control system for a drive unit of a hybrid vehicle of the invention further comprises a plurality of oil pumps, and a pump driving means for driving the oil pumps in case of driving the vehicle by the electric motor.

According to the invention, the plurality of oil pumps include a mechanical oil pump driven by the another power unit and an electrical oil pump, and the pump driving means includes a means for driving the another power unit, the mechanical oil pump, and the electrical oil pump by driving the electric motor.

In addition to above, according to the invention, the electric motor includes a motor generator which is rotated by a power inputted through the transmission to generate electric power. Here, the control system for a drive unit of a hybrid vehicle of the invention further comprises: an electric storage device connected with the motor generator; a detecting means for detecting a state of charge of the electric storage device; and an upshift commanding means for carrying out an upshifting of the transmission in case the detecting means detects that the state of charge of the electric storage device declines.

Moreover, according to the invention, the control system for a drive unit of a hybrid vehicle further comprises a speed change ratio maintaining means for maintaining a current speed change ratio of the transmission when a running mode of the vehicle is switched from a normal running in which the power is outputted from the another power unit, to a motor running in which the vehicle is run by the power of the electric motor; and a speed change ratio fixing means for shifting the speed change ratio of the transmission to the lowest speed side and fixing thereto, in case an output changing demand is outputted after the speed change ratio of the transmission is maintained.

In addition to above, the control system for a drive unit of a hybrid vehicle of the invention is characterized by further comprising: a differential gear mechanism having an input rotary element, an output rotary element and a reaction rotary element; and characterized in that the another power unit is connected with the input rotary element, an input member of the transmission and the electric motor are connected with the output rotary element, and the motor generator having a generating function is connected with the reaction rotary element.

The differential gear mechanism may be constructed of a planetary gear mechanism such as a single pinion type planetary gear mechanism and a double pinion type planetary gear mechanism, and the differential gear mechanism may be arranged in tandem with the transmission. Therefore, a total speed change ratio of the drive unit can be set by both of the differential gear mechanism and the transmission.

As explained above, the differential gear mechanism may be constructed of a planetary gear mechanism. In this case, a carrier can be used as the input rotary element by connecting the carrier with the another power unit, a sun gear can be used as the reaction rotary element by connecting the sun gear with the electric motor having a generating function, and a ring gear can be used as the output rotary element by connecting the ring gear with the transmission.

The transmission may be constructed of two sets of planetary gear mechanisms such as a single pinion type planetary gear mechanism or the like. In this case, the sun gears are connected with each other, and the carrier of one of the planetary gear mechanisms is connected with the ring gear of the other planetary gear mechanism. Those sun gears, carrier, and ring gear may be connected with the output element. In addition, a first clutch mechanism may be provided between the ring gear of one of the planetary gear mechanisms and the output rotary element of the differential gear mechanism, and a second clutch mechanism may be provided between the mutually connected sun gears and the output rotary element. Further, a first brake mechanism for fixing the sun gears selectively, and a second brake mechanism for fixing the carrier of the other planetary gear mechanism may be provided. The second brake mechanism may be constructed by arranging a unidirectional engagement device and a bidirectional engagement device in parallel with each other.

As explained above, according to the invention, a speed change operation of the transmission will not be carried out in case the vehicle is being run by the power of the electric motor. Therefore, an abrupt change in the drive force or in the revolution frequency of the electric motor, as well as shift shocks can be prevented or minimized.

Also, according to the invention, a speed change operation of the transmission is restricted in case the vehicle is being run by the power of the electric motor. Therefore, an abrupt change in the drive force or in the revolution frequency of the electric motor, as well as shift shocks can be prevented or minimized.

In addition to the above advantages, according to the invention, relatively large driver force can be ensured.

Also, according to the invention, the speed change ratio can be maintained to the lowest speed side by engaging the bidirectional engagement device arranged in parallel with the unidirectional engagement device, even when the vehicle is running but not driven by the prime mover. For this reason, a power source braking force can be ensured, and a regeneration amount of energy can be increased.

In case of driving the vehicle by the power of the electric motor, a heating value of the electric motor is increased. However, according to the invention, a plurality of oil pumps is driven in this case so that sufficient amount of lubricating oil can be ensured. Therefore, the electric motor can be cooled sufficiently by the sufficient amount of the lubricating oil.

Moreover, according to the invention, said another power unit and the mechanical oil pump connected thereto are not driven at the normal motor running time. Therefore, a power loss can be reduced, and the oil amount can be increased by driving the mechanical oil pump in case the temperature of the transmission is too high. For this reason, the transmission and the electric motor can be cooled and lubricated sufficiently.

Further, according to the invention, an upshifting of the transmission is carried out in case the state of charge of the electric storage device, which stores the power of the motor generator and feeds the power to the motor generator, is degraded. Therefore, although the revolution frequencies of the motor generator and the another power unit are lowered relatively when decelerating to establish power source braking, the power source braking force can be ensured by raising regenerative torque of the motor generator, and drop in the charging amount can be prevented by raising the generating amount of the motor generator to increase the charging amount of the electric storage device.

Furthermore, according to the invention, in case of shifting the speed change ratio to the lowest speed side to drive the vehicle by the power of the electric motor, the speed change ratio of just before the shifting is maintained first of all, and then the speed change ratio is shifted to lowest speed side when the output changing demand is outputted. Thus, a speed change operation is carried out while changing the output. That is, the change in the drive force resulting from a speed change operation is camouflaged with the change in the drive force resulting from the change of the output. In other words, the change in the drive force resulting from a speed change operation occurs when the driver is feeling the change in the drive force. For this reason, uncomfortable feeling is prevented, and in addition, a busy shift is avoided.

Additionally, according to the invention, the above explained advantages can also be achieved also in a hybrid drive unit, in which a power of said another power unit such as an internal combustion engine is distributed to the motor generator and to the transmission through the differential gear mechanism, and in which the power is transmitted to the transmission by driving the electric motor by the power generated by the motor generator.

FIG. 1 is a flowchart explaining one example of the control carried out by the control system of the invention.

FIG. 2 is a flowchart explaining another example of the control carried out by the control system of the invention.

FIG. 3 is a flowchart explaining still another example of the control carried out by the control system of the invention.

FIG. 4 is a flowchart explaining still another example of the control carried out by the control system of the invention.

FIG. 5 is a skeleton diagram showing one example of a drive unit for a hybrid vehicle to which the invention is applied.

FIG. 6 is a table showing a relation between gear stages set by a geared transmission and engagement states of hydraulic frictional engagement devices.

FIG. 7 is a nomographic diagram explaining operating states of individual transmissions shown in FIG. 5 .

Next, this invention will be described in connection with its specific examples. A drive unit of a hybrid vehicle to which the invention is applied will be explained first of all. As illustrated in FIG. 5 , the drive unit of a hybrid vehicle (as will be called the “drive unit” hereinafter) 10 comprises, an input shaft 14 as an input rotary member arranged coaxially in a non-rotatable transmission case 12 (as will be called as a case 12 hereinafter) mounted on a vehicle, a continuously variable transmission unit 11 connected to the input shaft 14 directly or indirectly through a not shown pulsation absorbing damper (i.e., a vibration dampening device), a geared transmission unit 20 functioning as a geared transmission connected in tandem through a transmission member (i.e., a transmission shaft) 18 on a power transmission route between the continuously variable transmission unit 11 and a (not shown) driving wheel, and an output shaft 22 as an output rotary member connected to the geared transmission unit 20 . The above-listed elements are arranged in tandem in the drive unit 10 . This drive unit 10 is suitable for front-engine rear-drive vehicles in which elements are arranged in tandem, and the transmission 10 is arranged between an engine as a prime mover for running and a pair of driving wheels. The prime mover is an engine 8 exemplified by a gasoline engine and a diesel engine or the like, and the engine 8 is connected directly with the input shaft 14 or indirectly through a not shown pulsation absorbing damper. This engine 8 corresponds to an another drive unit of the invention. Here, since the arrangement of the drive unit 10 is symmetrical with respect to its axial line, a lower part thereof is omitted in the skeleton diagram of FIG. 5 .

The continuously variable transmission unit 11 is a mechanism for mechanically distributing an output of the engine 8 inputted to the input shaft 14 . The continuously variable transmission unit 11 comprises a power distribution mechanism 16 functioning as a differential mechanism for distributing the output of the engine 8 to the first electric motor MG 1 and to the transmission member 18 , and a second electric motor MG 2 arranged to rotate integrally with the transmission member 18 . According to this embodiment, both electric motors MG 1 and MG 2 are motor generators having a function to generate electric power. More specifically, the first electric motor MG 1 intrinsically has a function as a generator for generating a reaction force, and the second electric motor MG 2 intrinsically has a function as a motor for outputting a driving force for running the vehicle. The second electric motor MG 2 corresponds to an electric motor of the invention.

The power distributing mechanism 16 comprises a single pinion type first planetary gear mechanism 24 the gear ratio thereof is e.g., approximately “0.418” and it is represented by “ρ 1 ”. The first planetary gear mechanism 24 comprises following rotary elements, such as a first sun gear S 1 , a first planetary gear P 1 , a first carrier CA 1 holding the first planetary gear P 1 in a rotatable and revolvable manner, and a first ring gear R 1 meshing with the first sun gear S 1 through the first planetary gear P 1 . The aforementioned gear ratio ρ 1 is expressed as ZS 1 /ZR 1 . Here, ZS 1 represents a teeth number of the first sun gear S 1 , and ZR 1 represents a teeth number of the first ring gear R 1 .

In the power distribution mechanism 16 , the first carrier CA 1 is connected to the input shaft 14 , i.e., to the engine 8 , the first sun gear S 1 is connected to the first electric motor MG 1 , and the first ring gear R 1 is connected to the transmission member 18 . A differential action of the power distribution mechanism 16 is achieved by allowing to rotate three elements of the first planetary gear mechanism 24 , i.e., to rotate the first sun gear S 1 , the first carrier CA 1 and the first ring gear R 1 relatively among each other. As a result, the output of the engine 8 is distributed to the first electric motor MG 1 and to the transmission member 18 , and a part of the distributed power of the engine 8 is converted into an electric power by the first electric motor MG 1 . The electric power is stored or used to drive the second electric motor MG 2 . In consequence, the continuously variable transmission unit 11 (or the power distribution mechanism 16 ) functions as an electrical differential mechanism. That is, the continuously variable transmission unit 11 achieves a “continuously variable transmission state (i.e., an electrical CVT state)”, so that the revolution frequency of the engine 8 is varied continuously without varying the revolution frequency of the transmission member 18 . In short, when the power distribution mechanism 16 is performing the differential action, the continuously variable transmission unit 11 is also performing the differential action. Specifically, the continuously variable transmission unit 11 functions as an electrical continuously variable transmission, in which its speed change ratio Y 0 (i.e., revolution frequency of the input shaft 14 or revolution frequency of the transmission member 18 ) is varied continuously from a minimum value Y 0 min to a maximum value Y 0 max.

The geared transmission unit 20 comprises: a single pinion type second planetary gear mechanism 26 the gear ratio thereof is e.g., approximately “0.532”, and it is represented by “ρ 2 ”; and a single pinion type third planetary gear mechanism 28 the gear ratio thereof is e.g., approximately “0.418”, and it is represented by “ρ 3 ”. A second sun gear S 2 of the second planetary gear mechanism 26 and a third sun gear S 3 of the third planetary gear mechanism 28 are connected integrally with each other, and a second clutch C 2 is arranged between those sun gears S 2 and S 3 and the transmission member 18 . Also, a first brake B 1 for fixing the sun gears S 2 and S 3 integrally is arranged between the sun gears S 2 and S 3 and the case 12 . A second carrier CA 2 of the second planetary gear mechanism 26 and a third ring gear R 3 of the third planetary gear mechanism 28 are connected integrally with each other. Those carrier CA 2 and ring gear R 3 are connected to the output shaft 22 . On the other hand, there is provided a first clutch C 1 connecting a second ring gear R 2 selectively to the transmission member 18 . Further, a second brake B 2 and a one-way clutch F 1 is provided as means for connecting a third carrier CA 3 of the third planetary gear mechanism 28 selectively to the case 12 and fixing thereto. Here, the one-way clutch F 1 is engaged to fix the third carrier CA 3 in case a torque acts on the third carrier CA 3 in the direction to rotate it backwardly, i.e., in the rotational direction opposite to the rotational direction of the engine 8 .

The aforementioned first clutch C 1 , second clutch C 2 , first brake B 1 , and second brake B 2 are hydraulic frictional engagement devices generally used in the conventional automatic transmissions for a vehicle. Those hydraulic frictional engagement devices are composed mainly of a wet multiple disc clutch in which a plurality of frictional discs facing with each other are pressed by a hydraulic actuator, a band brake in which one of the end of one or two band(s) applied to an outer circumferential face of a rotating drum is (are) wound up by a hydraulic actuator, and so on. The role of the hydraulic frictional engagement device is to connect the members of both sides thereof selectively.

In order to generate oil pressure for controlling and lubricating the hydraulic frictional engagement devices, and for cooling the electric motors MG 1 and MG 2 , there are provided two of oil pumps PO 1 and OP 2 . One of the oil pumps OP 1 is a mechanical oil pump and connected to the engine 8 to be driven by the engine 8 . The other oil pump is an electrical oil pump driven by the motor 30 .

According to the drive unit 10 thus far explained, as indicated in the table of FIG. 6 , any of a first gear stage (represented as 1st in the table) to a fourth gear stage (represented as 4th in the table), a reverse gear stage (represented as R in the table), and a neutral (represented as N in the table) are achieved by selectively activating the aforementioned elements, specifically, by selectively engaging the first clutch C 1 , the second clutch C 2 , the first brake B 1 , the second brake B 2 and the one-way clutch F 1 . As a result, a speed change ratio Y (i.e., input shaft revolution NIN/output shaft revolution NOUT), which changes substantially in equal ratio at every gear stage is obtained. Here, In FIG. 6 , “◯” represents an “engagement” of the element, a blank means that the element is released, and “(◯)” represents that the element is engaged when applying a power source braking.

The continuously variable transmission 11 functions as a continuously variable transmission, and the geared transmission unit 20 arranged in tandem therewith functions as a geared transmission. As a result, the input revolution to the geared transmission unit 20 , more specifically, the revolution frequency of the transmission member 18 to be inputted individually to the first to fourth gear stages of the geared transmission unit 20 is varied continuously, and the individual gear stages thereby obtain a continuous range of the speed change ratio. For this reason, the speed change ratio can be varied steplessly and continuously even between the gear stages. Consequently, a speed change ratio YT achieved by the continuously variable transmission unit 11 and the geared transmission unit 20 , more specifically, a total speed change ratio YT as an entire speed change ratio of the drive unit 10 , which is governed by both of the speed change ratio Y 0 of the continuously variable transmission unit 11 and the speed change ratio Y of the geared transmission unit 20 , can be varied steplessly.

FIG. 7 is a nomographic diagram linearly indicating a relation of revolution frequencies of the rotary elements to be connected depending on the gear stage, in the drive unit 10 comprising the continuously variable transmission unit 11 functioning as a differential unit or a first transmission unit, and the geared transmission unit 20 functioning as a (an automatic) transmission unit or a second transmission unit. The nomographic diagram of FIG. 7 is a two-dimensional coordinate composed of abscissa axes indicating relations of the gear ratios “ρ” of individual planetary gear mechanisms 24 , 26 and 28 , and longitudinal axes indicating relative revolution frequencies. In the diagram, the bottom abscissa axis X 1 represent “zero” revolution, and the middle abscissa axis X 2 represents the revolution frequency of “1.0”, i.e., a revolution frequency Ne of the engine 8 connected with the input shaft 14 , and an abscissa axis XG represents a revolution frequency of the transmission member 18 .

Meanwhile, three longitudinal axes Y 1 , Y 2 and Y 3 individually indicates relative revolution frequencies of three elements of the power distribution mechanism 16 of the continuously variable transmission unit 11 . Specifically, Y 1 indicates relative revolution frequency of the first sun gear S 1 corresponding to a second rotary element (or a second element) RE 2 , Y 2 indicates relative revolution frequency of the first carrier CA 1 corresponding to a first rotary element (or a first element) RE 1 , and Y 3 indicates relative revolution frequency of the first ring gear R 1 corresponding to a third rotary element (or a third element) RE 3 . Clearances between those longitudinal axes Y 1 to Y 3 are determined individually in accordance with a gear ratio ρ 1 of the first planetary gear mechanism 24 . Four longitudinal axes Y 4 to Y 7 individually represent the rotary elements of the geared transmission unit 20 . Specifically, Y 4 represents the mutually connected second sun gear S 2 and third sun gear S 3 corresponding to a fourth rotary element (or a fourth element) RE 4 , Y 5 represents the third carrier CA 3 corresponding to a fifth rotary element (or a fifth element) RE 5 , Y 6 represents the mutually connected second carrier CA 2 and third ring gear R 3 corresponding to a sixth rotary element (or a sixth element) RE 6 , and Y 7 represents the second ring gear R 2 corresponding to a seventh rotary element (or a seventh element) RE 7 . Clearances between those longitudinal axes Y 4 to Y 7 are determined individually in accordance with a gear ratios ρ 2 and ρ 3 of the second and third planetary gear mechanisms 26 and 28 . Provided that the clearance between the longitudinal axes representing the sun gear and the carrier is set to “1”, the clearance between the longitudinal axes representing the carrier and the ring gear indicates the gear ratio ρ of the planetary gear mechanism. Specifically, in the continuously variable transmission unit 11 , the clearance between the longitudinal axes Y 1 and Y 2 is set to “1”, and the clearance between Y 2 and Y 3 is set to the gear ratio ρ 1 . In the second and third planetary gear mechanisms 26 and 28 of the geared transmission unit 20 , also, each clearance between the sun gear and the carrier is set to “1” and each clearance between the carrier and the ring gear is set to “ρ”.

As can be seen from the nomographic diagram in FIG. 7 , in the power distribution mechanism 16 (or the continuously variable transmission unit 11 ) of the drive unit 10 of this embodiment, the first rotary element RE 1 (or the first carrier CA 1 ) of the first planetary gear mechanism 24 is connected to the input shaft 14 , i.e., to the engine 8 , the second rotary element RE 2 is connected to the first electric motor MG 1 , and the third rotary element RE 3 (or the first ring gear R 1 ) is connected to the transmission member 18 and to the second electric motor MG 2 . Therefore, a power is transmitted (i.e., inputted) from the input shaft 14 to the geared transmission unit 20 via the transmission member 18 . The relation between the revolution frequencies of the first sun gear S 1 and the first ring gear R 1 is indicated by a slant line L 0 passing through an intersection of Y 2 with X 2 .

Since the first planetary gear mechanism 24 performs a differential action, the revolution frequency of the first ring gear R 1 indicated at the intersection of the line L 0 with the longitudinal axis Y 3 is fluctuated, if the revolution frequency of the first sun gear S 1 indicated at the intersection of the line L 0 with the longitudinal axis Y 1 is fluctuated by controlling the reaction force resulting from a generation of the first electric motor MG 1 .

On the other hand, in the geared transmission unit 20 , the fourth rotary element RE 4 is connected selectively to the transmission member 18 through the second clutch C 2 and selectively to the case 12 through the first brake B 1 , the fifth rotary element RE 5 is connected selectively to the case 12 through the second brake B 2 , the sixth rotary element RE 6 is connected selectively to the case 12 through the third brake B 3 , and the seventh rotary element RE 7 is connected to the output shaft 22 .

As shown in FIG. 6 , in the geared transmission unit 20 , a revolution frequency of the output shaft 22 at the first gear stage is indicated at the intersection of the slant line L 1 with the longitudinal axis Y 6 indicating the revolution frequency of the sixth rotary element RE 6 connected to the output shaft 22 . Here, the line L 1 is determined as a result of an engagement of the first clutch C 1 and the one-way clutch F 1 or the second brake B 2 , and it extends from the intersection of the longitudinal axis Y 5 indicating the revolution frequency of the fifth rotary element RE 5 with the abscissa axis X 1 , to the intersection of the longitudinal axis Y 7 indicating the revolution frequency of the seventh rotary element RE 7 with the abscissa axis X 2 . As in the case of the first gear stage: a revolution frequency of the output shaft 22 at the second gear stage is indicated at the intersection of the longitudinal axis Y 6 with a slant line L 2 determined as a result of engaging the first clutch C 1 and the first brake B 1 ; and a revolution frequency of the output shaft 22 at the third gear stage is indicated at the intersection of the longitudinal axis Y 6 with a horizontal line L 3 determined as a result of engaging the first clutch C 1 and the second clutch C 2 . If the first sun gear S 1 is fixed by the first electric motor MG 1 , the power from the continuously variable transmission unit 11 is inputted at the revolution frequency higher than the revolution frequency NE of the engine 8 . Therefore, a revolution frequency of the output shaft 22 at the fourth gear stage is indicated at the intersection of the longitudinal axis Y 6 with a horizontal line L 4 determined as a result of engaging the first clutch C 1 and the second clutch C 2 .

As explained above, the drive unit 10 of the invention comprises: the continuously variable transmission unit 11 , in which a speed change ratio thereof is varied in accordance with the revolution frequency of the first electric motor MG 1 ; and the geared transmission unit 20 , in which a gear ratio thereof is changed according to the change in a power transmitting point, more specifically, according to the change in a power transmitting route which is changed depending on the engagement and releasing status of the clutches C 1 and C 2 , and brakes B 1 and B 2 . Therefore, the total speed change ratio is controlled to vary continuously as much as possible. For this purpose, in case of carrying out a shifting operation of the geared transmission unit 20 , the continuously variable transmission unit 11 (i.e., a revolution frequency of the first electric motor MG 1 ) is controlled to vary the speed change ratio thereof in the direction opposite to the change in the gear ratio of the geared transmission unit 20 .

In this case, the shifting operation of the geared transmission unit 20 is carried out by feeding the oil pressure to any of the clutches C 1 and C 2 or any of the brakes B 1 and B 2 , or draining the oil pressure therefrom. On the other hand, the speed change operation of the continuously variable transmission unit 11 is carried out by electrically controlling the revolution frequency of the first electric motor MG 1 . Therefore, a speed changing rate of the continuously variable transmission unit 11 is faster than a shifting rate of the geared transmission unit 20 . For this reason, the speed change operation of the continuously variable transmission unit 11 is carried out in accordance with a progression of the shifting operation of the geared transmission unit 20 .

Specifically, the power of the engine 8 is inputted to the carrier CA 1 of the first planetary gear mechanism 24 in the continuously variable transmission unit 11 , and the power is distributed to the sun gear S 1 and to the ring gear R 1 . In this situation, if the first electric motor MG 1 is operated as a generator, the first electric motor MG 1 establishes a reaction force against the sun gear S 1 . As a result, the ring gear R 1 is rotated according to the revolution frequency of the sun gear S 1 . That is, provided that the revolution frequency of the ring gear R 1 is constant, the revolution frequency of the engine 8 can be controlled by the first electric motor MG 1 . Therefore, the substantial speed change ratio of the continuously variable transmission unit 11 is varied continuously by changing the revolution frequency of the engine 8 continuously.

Under the driving state, the electric power is thus generated by the first electric motor MG 1 , and the generated electric power is supplied to the second electric motor MG 2 . Consequently, the second electric motor MG 2 is driven as a motor and the torque is transmitted to the transmission member 18 . In order to carry out this kind of control, the first and the second electric motors MG 1 and MG 2 are connected to the electric storage device 41 thorough a (not shown) controller. Here, it is possible to feed the electric power to a motor 30 driving the oil pump OP 2 from the electric storage device 41 . Alternatively, it is also possible to supply the electric power selectively to the motor 30 by providing a not shown another electric storage device 41 .

A speed change operation of the continuously variable transmission unit 11 is carried out by obtaining a target revolution to achieve the total speed change ratio determined on the basis of an output demand detected from a depression of a (not shown) accelerator pedal, and by controlling the first electric motor MG 1 to achieve the target revolution in first order lag. Alternatively, a speed change operation of the continuously variable transmission unit 11 is carried out by setting a transitional target revolution for achieving the target revolution, and by controlling the first electric motor MG 1 to vary the transitional target revolution to approximate to the target revolution sequentially. This kind of control of the speed change ratio is executed by a command signal from an electronic control unit (ECU) 40 . For this purpose, a various kinds of data, e.g., a vehicle speed, an opening degree of an accelerator (i.e., an output demand), a shift position, a revolution frequency of the first electric motor MG 1 are inputted to the electronic control unit 40 . Also, data such as a speed change diagram in which a speed change ratio is set in accordance with the running condition is stored in the electronic control unit 40 in advance.

The above-mentioned drive unit 10 is capable of carrying out a so-called “Motor Running (i.e., EV Running)”. EV running is a running mode in which the vehicle is run by the power of any of the electric motors MG 1 and MG 2 while halting the engine 8 . For this purpose, there is provided an EV switch 42 for selecting the EV running, and a signal for the EV running is inputted from the electronic control unit 40 . A drive force under the EV running and a duration time of the EV running are smaller and shorter in comparison with those under the normal running mode in which the vehicle is run by driving the engine 8 . Also, a thermal load on the electric motors MG 1 and MG 2 are larger than that under the normal running. Therefore, according to the control system of the invention, the following control is carried out.

FIG. 1 is a flowchart explaining one example the control. First of all, it is judged whether or not the EV running mode is selected, that is, it is judged whether or not the EV switch 42 is ON (at Step S 1 ). In case the answer of Step S 1 is NO, the routine is returned without carrying out any specific control. To the contrary, in case the answer of Step S 1 is YES, the first gear stage of the geared transmission 20 is set to apply an engine brake (i.e., a power source braking) (at Step S 2 ). Specifically, as shown in FIG. 7 , the second brake B 2 is engaged with the one-way clutch F 1 arranged in parallel therewith. Accordingly, the second brake B 2 corresponds to the bidirectional engagement device of the invention.

Then, the gear stage of the geared transmission (or AT unit) 20 is fixed to the first gear stage (at Step S 3 ). In case the vehicle speed is increased under the normal running mode, the total speed change ratio, i.e., the entire speed change ratio of the drive unit 10 is shifted upwardly to the high speed side, and an upshifting of the geared transmission 20 is carried out in response to the upshifting of the total speed change ratio. However, in case the EV running mode is selected, the gear stage of the geared transmission 20 is fixed to the first gear stage at Step S 3 , by inhibiting or restricting an upshifting of the geared transmission 20 .

The total speed change ratio is shifted upwardly to the high speed side according to a rise in the vehicle speed even under the EV running mode. Therefore, a speed change operation of the continuously variable transmission unit 11 is carried out in accordance with the running condition of the vehicle such as a vehicle speed (at Step S 4 ). Specifically, the engine 8 is halted under the EV running mode, therefore, the ring gear R 1 and the transmission member 18 connected therewith is rotated in the forward direction by rotating the first electric motor MG 1 . In this situation, the vehicle is run by the powers of the first and the second electric motors MG 1 and MG 2 by operating the second electric motor MG 2 to apply the torque to the transmission member 18 . Therefore, in case the vehicle speed is increased, the revolution frequencies of the ring gear R 1 and the transmission member 18 connected therewith are raised by reducing the revolution frequency of the first electric motor MG 1 , i.e., by raising the revolution frequency of the first electric motor MG 1 in the backward direction. To the contrary, in case the vehicle speed is lowered, the revolution frequencies of the ring gear R 1 and the transmission member 18 connected therewith are lowered by raising the revolution frequency of the first electric motor MG 1 , i.e., by reducing the revolution frequency of the first electric motor MG 1 in the backward direction. For example, this control is carried out by preparing a speed change map for the EV running mode in advance, by obtaining a total speed change ratio from the detected running condition and the speed change map, and by controlling the revolution frequency of the first electric motor MG 1 and the torque of the second electric motor MG 2 to achieve the total speed change ratio.

Therefore, a shifting operation of the geared transmission 20 will not be carried out under the EV running mode by carrying out the control shown in FIG. 1 . For this reason, it is possible to prevent shocks resulting from the stepwise change in the speed change ratio. As explained, the first gear stage of the geared transmission 20 is the lowest side gear stage where the gear ratio thereof is largest. Therefore, the torque inputted to the geared transmission 20 can be amplified to be outputted to the output shaft 22 . As a result, the drive force for the entire vehicle can be ensured.

As explained above, the thermal loads on the electric motors MG 1 and MG 2 are increased under the EV running mode, in comparison with those under the normal running mode. However, the oil is commonly used for cooling the electric motors MG 1 and MG 2 and for lubricating the geared transmission 20 . That is, the oil temperature tends to be raised under the EV running mode. For this reason, the control system of the invention carries out the control shown in FIG. 2 . Specifically, in case the EV running mode is selected, i.e., in case the answer of Step S 11 in FIG. 2 is YES, it is judged whether or not the oil temperature of the geared transmission 20 is higher than a predetermined allowable oil temperature (at Step S 12 ). In case the answer of Step S 11 is NO, the routine is returned without carrying out any specific control.

The allowable oil temperature is a temperature set in advance to maintain the temperatures of the electric motors MG 1 and MG 2 lower than an upper limit. In case the detected temperature exceeds the allowable oil temperature so that the answer of Step S 12 is YES, the first electric motor MG 1 is activated (at Step S 13 ). In case the answer of Step S 12 is NO, the routine is returned without carrying out any specific control.

Basically, the first electric motor MG 1 is activated to control a speed change operation of the continuously variable transmission unit 11 , however, at Step S 13 , the first electric motor MG 1 is activated to increase the oil amount in addition to the aforementioned fundamental role. That is, since the first planetary gear mechanism 24 constituting the continuously variable transmission 11 performs a differential action among the engine 8 , the first electric motor MG 1 and the transmission member 18 , the revolution frequency of the engine 8 can be controlled by the revolution frequency of the first electric motor MG 1 . Specifically, the revolution frequency of the engine 8 is increased by raising (or lowering in the backward direction) the revolution frequency of the first electric motor MG 1 higher than the revolution thereof where the engine 8 is halted when the vehicle is running under the EV running mode. Namely, the engine 8 is rotated concurrently to drive the mechanical oil pump OP 1 connected therewith (at Step S 14 ).

Basically, the lubrication oil is fed to the geared transmission unit 20 and circulated therein by driving the mechanical oil pump OP 2 by the motor 30 . However, even in case the amount of the lubrication oil is relatively insufficient and the oil temperature is thereby raised, the lubrication oil can be further fed to the geared transmission unit 20 by driving the mechanical oil pump OP 1 , which is basically driven by the engine 8 , by the first electric motor MG 1 . For this reason, sufficient amount of the lubrication oil can be ensured in the geared transmission unit 20 . Therefore, the electric motors MG 1 and MG 2 can be cooled by the ensured lubrication oil so that an overheating of the electric motors MG 1 and MG 2 can be prevented. As a result, the EV running mode can be continued.

As mentioned above, the vehicle is run by the electric power of the electric storage device 41 under the EV running mode. Therefore, it is preferable to ensure the charging amount by carrying out a regeneration of energy as much as possible in case the EV running mode is selected. For this purpose, according to the invention, the following control can be carried out by detecting a state where the regeneration of energy can be carried out, e.g., by detecting a state where the vehicle is decelerated.

FIG. 3 is a flowchart explaining an example of the above-mentioned control. First of all, it is judged whether or not the EV running mode is selected, specifically, whether or not the EV switch is ON (at Step S 21 ). In case the answer of Step S 21 is YES, the revolution frequency of the first electric motor MG 1 is fixed when the shifting operation of the geared transmission unit 20 is carried out, and the revolution frequency of the engine 8 is allowed to be changed in connection with fixing the revolution frequency of the first electric motor MG 1 (at Step S 22 ). Then, it is judged whether or not the electric storage device 41 can accept the electric power, that is, an amount of the electric power stored in the electric storage device 41 is within an allowable range to accept the electric power to be charged (at Step S 23 ).

In case the answer of Step S 23 is NO, the routine is returned without carrying out any specific control. To the contrary, in case the answer of Step S 23 is YES, a judgment of regeneration is carried out, that is, it is judged whether or not the running condition of the vehicle is a condition where a regeneration of energy can be carried out (at Step S 24 ). This judgment can be made based on the fact that the output demand becomes zero, e.g., based on the fact that a (not shown) accelerator pedal is returned when the vehicle is running at a speed higher than a predetermined speed.

In case the answer of Step S 24 is NO, the routine is returned without carrying out any specific control. Consequently, the gear stage of the geared transmission unit 20 is kept to the first gear stage by the aforementioned control shown in FIG. 1 . To the contrary, in case the answer of Step S 24 is YES, specifically, in case the regeneration of energy can be carried out, the control to fix the gear stage of the geared transmission unit 20 to the first gear stage is cancelled and the geared transmission unit 20 is shifted upwardly (at Step S 25 ). For example, the geared transmission unit 20 is shifted to the second gear stage. When the geared transmission unit 20 is shifted upwardly, the revolution frequency of the transmission member 18 of the input side is lowered. Therefore, the regenerative torque of the second electric motor MG 2 is increased in order to maintain the engine braking force and to increase a regeneration amount. At least a part of the electric power thus obtained is fed to the electric storage device 41 and stored therein.

Thus, the regeneration of energy is promoted to obtain the electric energy under the EV running mode where the vehicle is run by the electric power. For this reason, duration of the EV running mode can be prolonged.

If the state of charge (SOC) of the electric storage device 41 is low when the vehicle is running under the EV running mode, the engine 8 is driven to generate an electric power. The generated electric power is used to drive the vehicle and also stored into the electric storage device 41 . In this case, the geared transmission unit 20 is fixed to the first gear stage under the EV running mode. However, the control system of the invention is adapted to carry out a control shown in FIG. 4 in order to prevent or minimize the shocks resulting from a downshifting to the first gear stage.

FIG. 4 shows an example of the control to carry out a downshifting of the geared transmission unit 20 to carry out the EV running mode. First of all, it is judged whether or not the state of charge (SOC) of the electric storage device 41 is lower than a predetermined acceptable value (at Step S 41 ). In case the answer of Step S 41 is NO, the routine is returned without carrying out any specific control. To the contrary, in case the answer of Step S 41 is YES, the engine 8 is started (at Step S 42 ). Specifically, a motoring of the engine 8 is carried out by the first electric motor MG 1 or a (not shown) starter motor, and a fuel is fed to the engine 8 simultaneously.

Then, it is judged whether or not the output demand is changed (at Step S 43 ). This judgment can be made based on the fact that the not shown accelerator pedal is operated. In case the answer of Step S 43 is NO, specifically, in case the output demand is not changed, the gear stage of the geared transmission unit 20 is kept to the current gear stage (at Step S 44 ). Then, the routine is returned. To the contrary, in case the answer of Step S 43 is YES, a downshifting of the geared transmission unit 20 is carried out and the gear stage is fixed to the first gear stage (at Step S 45 ).

Thus, according to the control shown in FIG. 4 , a shifting operation of the geared transmission unit 20 to the first gear stage will not be executed only by shifting the running mode from the normal running mode to the EV running mode. That is, a shifting operation of the geared transmission unit 20 to the first gear stage is executed when the output demand is changed. This means that the shifting operation is executed at a timing to operate the accelerator or the like, as the case of executing the shifting operation under the normal running mode. For this reason, the driver will not feel an uncomfortable feeling.

Here will be briefly explained a relation between the aforementioned examples and the invention. The functional means of Step S 3 shown in FIG. 1 corresponds to the speed change inhibiting means and the speed change restricting means of the invention. The functional means of Steps S 13 and S 14 shown in FIG. 2 correspond to the pump driving means of the invention. The functional means of Step S 25 shown in FIG. 3 corresponds to the upshift commanding means of the invention. The functional means of Step S 44 shown in FIG. 4 corresponds to the speed change ratio maintaining means of the invention. The functional means of Step S 45 shown in FIG. 4 corresponds to the speed change ratio fixing means of the invention.

Here, the present invention should not be limited to the above-mentioned specific examples. Specifically, according to the invention, the transmission may be both geared transmission and continuously variable transmission. Moreover, in case of inhibiting or restricting a speed change operation, the gear stage may be fixed not only to the lowest gear stage but also to the other gear stage of lower side. Further, the motor running may be set not only manually by operating the switch but also by a signal from another suitable control system.

The present invention can be utilized in a field of manufacturing and repairing automobiles such as cars, and in a field of manufacturing and processing parts for automobiles.