Patent Application
20100191429
The present invention relates to a control device of a continuously variable transmission controlling a gear ratio of a continuously variable transmission mounted in a vehicle.
In a vehicle whereupon an engine (internal combustion engine) is mounted, an automatic transmission automatically and optimally setting a gear ratio between the engine and a drive wheel is known as a transmission for suitably transmitting torque and rotation speed generated by the engine to the drive wheel in accordance with a driving condition of the vehicle.
For example, a planetary gear type transmission setting a gear ratio (gear position) using a clutch and brake and a planetary gear device and a continuously variable transmission of belt-type (CVT) performing stepless adjustment of a gear ratio exist as an automatic transmission mounted in a vehicle.
A continuously variable transmission of belt-type has a belt wound around a primary pulley (input-side pulley) and a secondary pulley (output-side pulley) having a pulley groove (V-groove) and is configured such that a gear ratio is set in a stepless fashion by simultaneously expanding a groove width of the pulley groove of one of the pulleys and contracting a groove width of the pulley grove of the other pulley so as to continuously vary a winding radius (effective diameter) of the belt with respect to each of the pulleys. A torque transmitted in this continuously variable transmission of belt-type is a torque corresponding to a load acting in a direction in which the belt and the pulleys are made to contact mutually, and therefore, in order to apply tension to the belt, the belt is clamped by the pulleys.
Furthermore, as explained above, a speed change of a continuously variable transmission of belt-type is carried out by expanding and contracting the groove widths of the pulley grooves. Specifically, each of the primary pulley and the secondary pulley comprises a fixed sheave and a moveable sheave, and a speed change is carried out by moving the moveable sheave forwards and backwards in an axial direction using a hydraulic actuator provided at a rear face side thereof.
In this way, in a continuously variable transmission of belt-type, the belt is clamped by the pulleys in order to apply tension to the belt, and in addition, the condition of clamping of the belt by the pulleys is changed in order to carry out a speed change. Accordingly, the groove width of the primary pulley and the groove width of the secondary pulley are simultaneously changed by delivering hydraulic pressure corresponding to a required torque as typified by engine load, etc. to the hydraulic actuator at the secondary pulley side so as to secure a necessary transmission torque capacity and by delivering hydraulic pressure for carrying out a speed change to the hydraulic actuator at the primary pulley side.
Furthermore, in a vehicle wherein such a continuously variable transmission is mounted, a gear ratio map (see
Here, a technology described in Patent Citation 2 as mentioned hereinafter exists as a technology related to control of a speed change of a continuously variable transmission. The technology described in this Patent Citation 2 comprises a low-speed type shift schedule and a high-speed type shift schedule, and upon switching from the low-speed type shift schedule to the high-speed type shift schedule, a target engine rotation speed or a target drive pulley rotation speed is increased as a function of time from a point in time whereat changing of the shift schedule is determined to have occurred, thus preventing sudden changes in torque from occurring.
In speed change control of a continuously variable transmission, however, as the target gear ratio is calculated as explained above by referring to a gear ratio map, etc. as shown in
Taking such a point into consideration, transient control limiting a change amount of the gear change upon depression or return of the accelerator by foot is carried out, but even in this type of transient control, a static target moves, and therefore, it is not possible to limit the change amount of the gear change to such a degree that drivability can be improved.
It should be noted that the above-mentioned Patent Citation 2 only discloses a technology whereby, upon switching from the low-speed type shift schedule to the high-speed type shift schedule, the target engine rotation speed or the target drive pulley rotation speed is increased as a function of time from a point in time whereat changing of the shift schedule is determined to have occurred, thus preventing sudden changes in torque from occurring. In this Patent Citation 2, therefore, no consideration whatsoever is given to a change in the gear ratio upon depression or return of the accelerator by foot. Accordingly, even if the technology described in Patent Citation 2 is used, the above-explained problem cannot be resolved.
In light of such existing circumstances, it is an object of the present invention to provide, within a vehicle wherein a continuously variable transmission is mounted, a control device of the continuously variable transmission capable of improving responsiveness and drivability upon depression or return of the accelerator by foot.
In order to achieve the above object, the present invention provides a control device of a continuously variable transmission controlling a gear ratio of a continuously variable transmission mounted in a vehicle that is provided with a first target gear-ratio calculation means for calculating a first target gear ratio based on a driving condition of the vehicle (specifically, the vehicle speed and the accelerator opening amount) and a second target gear-ratio calculation means for calculating a second target gear ratio higher than the first target gear ratio based on a driving condition of the vehicle. Furthermore, it is characterized in that, with regard to a region wherein the first target gear ratio calculated by the first target gear-ratio calculation means is not more “high” than a gear ratio of the continuously variable transmission and the second target gear ratio calculated by the second target gear-ratio calculation means is not more “low” than the gear ratio of the continuously variable transmission, the gear ratio of the continuously variable transmission is held. It should be noted that a gear ratio described as “high” herein is a “small” gear ratio, and a gear ratio described as “low” herein is a “big” gear ratio.
A configuration wherein a lower limit of a low side of the gear ratio of the continuously variable transmission is guarded by adopting the first target gear ratio calculated by the first target gear-ratio calculation means as a current gear ratio of the continuously variable transmission when the first target gear ratio is more “high” than a previous gear ratio of the continuously variable transmission may be cited as a specific configuration of the present invention. Furthermore, a configuration wherein an upper limit of a high side of the gear ratio of the continuously variable transmission is guarded by adopting the second target gear ratio calculated by the second target gear-ratio calculation means as a current gear ratio of the continuously variable transmission when the second target gear ratio is more “low” than a previous gear ratio of the continuously variable transmission may be cited.
With the present invention, responsiveness to an accelerator operation upon depression or return of the accelerator by foot can be improved. This point is explained hereinafter.
First, in the present invention, the gear ratio of the continuously variable transmission is controlled using the first target gear ratio (for example, a target gear ratio prioritizing fuel efficiency) calculated by the first target gear-ratio calculation means when, for example, a target power (accelerator opening amount) changes to a decreasing side. During this speed change control, the first target gear ratio (“alpha”) will be more “high” (see
In this way, in a case wherein the target power reverses due to depression of the accelerator by foot when the target power (accelerator opening amount) is changing to a decreasing side, the power and drive force can be changed using only the engine torque by holding the gear ratio of the continuously variable transmission, and responsiveness and direct feel with respect to the accelerator operation are improved.
Furthermore, in the present invention, the gear ratio of the continuously variable transmission is controlled using the second target gear ratio calculated by the second target gear-ratio calculation means when, for example, a target power changes to an increasing side. During this speed change control, the second target gear ratio (“beta”) will be more “low” (see
In this way, in a case wherein the target power reverses due to a return operation of the accelerator by foot when the target power is changing to an increasing side, responsiveness to the accelerator operation can be improved by holding the gear ratio of the continuously variable transmission.
In the present invention, the first target gear ratio is calculated using a first map having a vehicle speed and an accelerator opening amount of the vehicle as a parameter, and the second target gear ratio is calculated using a second map having a vehicle speed and an accelerator opening amount of the vehicle as a parameter. Further, a configuration wherein the gear ratio of the continuously variable transmission is controlled based on the first target gear ratio (for example, a target gear ratio prioritizing fuel efficiency) calculated using the first map (up-use map) when the accelerator opening amount decreases and the gear ratio of the continuously variable transmission is controlled based on the second target gear ratio (for example, a target gear ratio prioritizing target power or drive force) calculated using the second map (down-use map) when the accelerator opening amount becomes higher can be employed.
It should be noted that the first target gear ratio and the second target gear ratio can be calculated using a map as explained above and can also be calculated using a first target gear-ratio calculating device and a second target gear-ratio calculating device.
With the present invention, responsiveness and drivability upon depression or return of the accelerator by foot in a vehicle wherein a continuously variable transmission is mounted can be improved.
The following is a description of the preferred embodiments of the present invention, with reference to the drawings.
The vehicle of this example is an FF (front-engine, front-drive) type vehicle whereupon an engine (internal combustion engine) 1 constituting a source of motive power for driving, a torque converter 2, a forward-reverse switching device 3, a continuously variable transmission (CVT) 4 of belt-type, a deceleration gear device 5, a differential gear device 6, and an ECU 8 (see
A crankshaft 11 constituting an output shaft of the engine 1 is connected to the torque converter 2, and an output of the engine 1 is transmitted from the torque converter 2 to the differential gear device 6 via the forward-reverse switching device 3, the continuously variable transmission 4 of belt-type, and the deceleration gear device 5 and is delivered to left and right drive wheels 7L, 7R.
These engine 1, torque converter 2, forward-reverse switching device 3, continuously variable transmission 4 of belt-type, and ECU 8 are described hereinafter.
The engine 1 is, for example, a multiple cylinder gasoline engine. A volume of intake air drawn into the engine 1 is adjusted by an electronic-control type throttle valve 12. The throttle valve 12 is capable of electronically controlling a degree of throttle opening independent of an accelerator-pedal operation of a driver, and that degree of opening (throttle-opening degree) is detected by a throttle-opening degree sensor 102. Furthermore, a temperature of a coolant of the engine 1 is detected by a coolant temperature sensor 103.
The throttle-opening degree of the throttle valve 12 is drive controlled by the ECU 8. In specific terms, the throttle-opening degree of the throttle valve 12 is controlled so as to acquire the optimum intake air volume (target air-intake volume) in accordance with an engine rotation speed NE detected by an engine rotation speed sensor 101, a degree of depression by foot of the accelerator pedal by the driver (accelerator opening amount Acc), and other operation conditions of the engine 1. In more specific terms, the actual throttle-opening degree of the throttle valve 12 is detected using the throttle-opening degree sensor 102, and a throttle motor 13 of the throttle valve 12 is feedback controlled in such a way that that actual throttle-opening degree matches the throttle-opening degree (target throttle-opening degree) at which the above-mentioned target air-intake volume is acquired.
The torque converter 2 is provided with an input-side pump impeller 21, an output-side turbine runner 22, and a stator 23 manifesting torque amplification functionality, etc., and performs transmission of motive power between the pump impeller 21 and the turbine runner 22 via a fluid. The pump impeller 21 is connected to the crankshaft 11 of the engine 1. The turbine runner 22 is connected to the forward-reverse switching device 3 via a turbine shaft 28.
The torque converter 2 is provided with a lock-up clutch 24 directly connecting the input side and the output side thereof. The pump impeller 21 and the turbine runner 22 rotate as one as a result of this lock-up clutch 24 being set to a fully engaged condition. Furthermore, as a result of the lock-up clutch 24 being engaged in a prescribed slip condition (semi-engaged condition), the turbine runner 22 rotates behind the pump impeller 21 with a prescribed amount of slip during driving. It should be noted that the torque converter 2 is provided with a mechanical-type oil pump (hydraulic pressure source) 27 driven through connection with the pump impeller 21.
The forward-reverse switching device 3 is provided with a double-pinion type planetary gear mechanism 30, a forward-travel clutch (input clutch) C1, and a reverse-travel brake B1.
A sun gear 31 of the planetary gear mechanism 30 is connected as one with the turbine shaft 28 of the torque converter 2, and a carrier 33 is connected as one with an input shaft 40 of the continuously variable transmission 4 of belt-type. Furthermore, this carrier 33 and sun gear 31 are selectively connected via the forward-travel clutch C1, and a ring gear 32 is configured so as to be selectively fixed to a housing via the reverse-travel brake B1.
The forward-travel clutch C1 and the reverse-travel brake B1 constitute hydraulic-type friction engagement elements engaged and disengaged by a hydraulic pressure control circuit 20 described hereinafter; as a result of the forward-travel clutch C1 being engaged and the reverse-travel brake B1 being disengaged, the forward-reverse switching device 3 adopts a rotation in unison condition and a forward-travel drive transmission channel is established (achieved); and in this condition, drive force in a forward-travel direction is transmitted to a side of the continuously variable transmission 4 of belt-type
Meanwhile, as a result of the reverse-travel brake B1 being engaged and the forward-travel clutch C1 being disengaged, a reverse-travel drive transmission channel is established (achieved) by the forward-reverse switching device 3. In this condition, the input shaft 40 rotates in an opposite direction with respect to the turbine shaft 28, and this drive force in a reverse-travel direction is transmitted to the side of the continuously variable transmission 4 of belt-type. Furthermore, when the forward-travel clutch C1 and the reverse-travel brake B1 are both disengaged, the forward-reverse switching device 3 will be neutral (cutoff condition), cutting off transmission of motive force.
The continuously variable transmission 4 of belt-type comprises an input-side primary pulley 41, an output-side secondary pulley 42, and a metal belt 43 wound around the primary pulley 41 and the secondary pulley 42, etc.
The primary pulley 41 is a variable pulley having a variable effective diameter and comprises a fixed sheave 411 fixed to the input shaft 40 and a moveable sheave 412 provided in a condition so as to be capable of sliding only in an axial direction of the input shaft 40. Similarly, the secondary pulley 42 is also a variable pulley having a variable effective diameter and comprises a fixed sheave 421 fixed to an output shaft 44 and a moveable sheave 422 provided in a condition so as to be capable of sliding only in an axial direction of the output shaft 44.
A hydraulic actuator 413 is disposed at the moveable sheave 412 side of the primary pulley 41 in order to change a V-groove width between the fixed sheave 411 and the moveable sheave 412. Furthermore, a hydraulic actuator 423 is similarly disposed also at the moveable sheave 422 side of the secondary pulley 42 in order to change a V-groove width between the fixed sheave 421 and the moveable sheave 422.
As a result of controlling a hydraulic pressure of the hydraulic actuator 413 of the primary pulley 41 in the continuously variable transmission 4 of belt-type of the above-described configuration, the respective V-groove widths of the primary pulley 41 and the secondary pulley 42 vary, a winding diameter (effective diameter) of the belt 43 changes, and the gear ratio (gear ratio=input-shaft rotation speed Nin/output-shaft rotation speed Nout) continuously changes. Furthermore, the hydraulic pressure of the hydraulic actuator 423 of the secondary pulley 42 is controlled such that the belt 43 is clamped with a prescribed clamping pressure whereat belt slipping does not occur. These controls are executed by the ECU 8 and the hydraulic pressure control circuit 20 (see
The hydraulic pressure control circuit 20 is provided with a linear solenoid valve and an on-off solenoid valve, etc., and by switching a hydraulic channel by controlling excitation and non-excitation of those solenoid valves, speed change control of the continuously variable transmission 4 of belt-type and engagement-disengagement control of the lock-up clutch 24, etc. are carried out. Excitation and non-excitation of the linear solenoid valve and the on-off solenoid valve of the hydraulic pressure control circuit 20 are controlled using a solenoid control signal (instruction hydraulic-pressure signal) from the ECU 8.
The ECU 8 is, as shown in
Various types of control program and maps, etc. referenced upon execution of those various types of control program are recorded in the ROM 82. The CPU 81 performs arithmetic processing based on the various types of control program and maps recorded in the ROM 82. Furthermore, the RAM 83 has memory for temporarily recording results of arithmetic operations of the CPU 81 and data input from each sensor, etc., and the back-up RAM 84 has non-volatile memory for recording data of the engine 1 to be stored upon stopping thereof, etc.
This CPU 81, ROM 82, RAM 83, and back-up RAM 84 are mutually connected via a bus 87, and in addition, are connected to an input interface 85 and an output interface 86.
The engine rotation speed sensor 101, the throttle-opening degree sensor 102, the coolant temperature sensor 103, a turbine rotation speed sensor 104, an input shaft rotation speed sensor 105, the vehicle speed sensor 106, the accelerator opening amount sensor 107, a brake pedal sensor 108, and a lever position sensor 109 detecting a lever position (operating position) of a shift lever 9, etc. are connected to the input interface 85 of the ECU 8, and the output signals of each of those sensors, in other words, the rotation speed (engine rotation speed) NE of the engine 1, a throttle-opening degree “theta”th of the throttle valve 12, a coolant water temperature Tw of the engine 1, a rotation speed (turbine rotation speed) NT of the turbine shaft 28, the rotation speed (input shaft rotation speed) Nin of the input shaft 40, a vehicle speed V, the operation amount (accelerator opening amount) Acc of an accelerator operation member such as the accelerator pedal, etc., an existence or non-existence (brake ON/OFF) of an operation of a foot brake constituting a normal-use brake, and a signal indicating a lever position (operation position) of the shift lever 9, etc. are provided to the ECU 8. The throttle motor 13, a fuel injection device 14, an ignition device 15, and the hydraulic pressure control circuit 20, etc. are connected to the output interface 86.
Here, of the signals provided to the ECU 8, the turbine rotation speed NT matches the input shaft rotation speed Nin during forward travel with the forward-travel clutch C1 of the forward-reverse switching device 3 engaged, and the vehicle speed V corresponds to the rotation speed (output shaft rotation speed) Nout of the output shaft 44 of the continuously variable transmission 4 of belt-type. Furthermore, the accelerator opening amount Acc indicates an output requirement amount of the driver.
Furthermore, the shift lever 9 is configured so as to be capable of being selectively operated to positions such as a parking position “P” for vehicle parking, a reverse position “R” for reverse travel, a neutral position “N” cutting off the transmission of motive force, a drive position “D” for forward travel, and a manual position “M” at which the gear ratio of the continuously variable transmission 4 of belt-type can be increased or decreased by a manual operation during forward driving, etc.
The manual position “M” is provided with a down-shift position and an up-shift position for increasing and decreasing the gear ratio or a plurality of range positions, etc. allowing selection of a plurality of speed change ranges with a different speed change range upper limit (side at which the gear ratio is small).
The lever position sensor 109 comprises a plurality of ON-OFF switches, etc. detecting operation of the shift lever 9 to, for example, the parking position “P”, the reverse position “R”, the neutral position “N”, the drive position “D”, and the manual position “M”, or the up-shift position and the down-shift position, or a range position, etc. It should be noted that, in order to change the gear ratio by a manual operation, a down-shift switch, an up-shift switch, or a lever, etc. can be provided on a steering wheel, etc independently of the shift lever 9.
Further, based on output signals, etc. from the above-described various sensors, the ECU 8 executes output control of the engine 1, speed change control of the continuously variable transmission 4 of belt-type, and gear-ratio calculation processing, etc. described hereinafter.
Output control of the engine 1 is performed by the throttle motor 13, the fuel injection device 14, the ignition device 15, and the ECU 8, etc. and speed change control of the continuously variable transmission 4 of belt-type, belt clamping force control, and control of engagement and disengagement of the lock-up clutch 24 are all performed by the hydraulic pressure control circuit 20. This throttle motor 13, fuel injection device 14, ignition device 15, and hydraulic pressure control circuit 20 are controlled by the ECU 8.
In speed change control of the continuously variable transmission 4 of belt-type, a target gear ratio is calculated using gear-ratio calculation processing described hereinafter, and a gear ratio is set based on that target gear ratio by performing speed change control of the continuously variable transmission 4 of belt-type, or in other words, control of a speed change control pressure through provision and discharge of operating oil with respect to the hydraulic actuator 413 of the primary pulley 41.
First, a gear-ratio map as shown in
In consideration of this type of point, this example is characterized in that, upon depression or return of the accelerator by foot, drivability (direct feel) and responsiveness with respect the accelerator operation are improved by holding the gear ratio of the continuously variable transmission and changing power and drive force using only an engine torque.
Hereinafter, a specific example of that control (gear-ratio calculation processing) is explained by way of reference to
First, a map used in the gear-ratio calculation processing of this example is explained by way of reference to
The map shown in
The map shown in
The down-use map Mb shown in
To explain in detail, when for example, the accelerator opening amount Acc (target power) changes with the progress of time, as shown in
Next, an example of speed change control of the continuously variable transmission 4 of belt-type is explained by way of reference to a flowchart of
In Step ST1, first of all, the vehicle speed V is read in from an output signal of the vehicle speed sensor 106 and the accelerator opening amount Acc is read in from an output signal of the accelerator opening amount sensor 107. Next, a low-side target gear ratio “alpha” is calculated using the sampled vehicle speed V and accelerator opening amount Acc and the up-use map Ma of
Next, in Step ST2, it is determined whether or not the target gear ratio “alpha” calculated this time (calculated in Step ST1) is more “high” than a previous gear ratio (actual gear ratio of the continuously variable transmission 4 of belt-type), and in a case where that determination result is a positive judgment, the procedure proceeds to Step ST4. In a case where the determination result of Step ST2 is a negative judgment, the procedure proceeds to Step ST3.
In Step ST4, the target gear ratio “alpha” calculated this time (calculated in Step ST1) is adopted as the target gear ratio for use in speed change control. After that, the procedure returns.
In Step ST3, it is determined whether or not the target gear ratio “beta” calculated this time (calculated in Step ST1) is more “low” than a previous gear ratio (actual gear ratio of the continuously variable transmission 4 of belt-type), and in a case where that determination result is a negative judgment, the procedure proceeds to Step ST5. In a case where the determination result of Step ST3 is a positive judgment, the procedure proceeds to Step ST6.
In Step ST5, the target gear ratio for use in speed change control of the continuously variable transmission 4 of belt-type is held at the previous gear ratio (actual gear ratio). After that, the procedure returns.
In Step ST6, the target gear ratio “beta” calculated this time (calculated in Step ST1) is adopted as the target gear ratio for use in speed change control of the continuously variable transmission 4 of belt-type. After that, the procedure returns.
Hereinafter, a more specific example of the above-explained gear-ratio calculation processing and speed change control is explained by way of reference to
First, when the accelerator opening amount Acc (target power) is changing to a small side, as shown in
As [Positive judgment in Step ST2]→[Step ST4] is sequentially repeated in the flowchart shown in
Next, if the accelerator is depressed by foot at a point in time TH1, the accelerator opening amount Acc (target power) reverses towards a large side, and therefore, a target gear ratio “alpha”x (not shown) calculated first after that reversal will be equal to or more “low” than the previous actual gear ratio (that is to say, a target gear ratio “alpha”H1 calculated immediately after depression of the accelerator by foot). At this point in time, or in other words, when the accelerator opening amount Acc (target power) reverses due to depression of the accelerator by foot, the gear ratio is held (Step ST5 of
Next, after reversal of the accelerator opening amount Acc (target power), at a point in time where the target gear ratio “beta” calculated using the down-use map Mb becomes equal to or more “low” than the gear ratio held as explained above (a point in time where the judgment of Step ST3 of
Here, if a hold region (period of time) A wherein the gear ratio of the continuously variable transmission 4 of belt-type is held is too long, the drive force (power) and fuel efficiency may deteriorate, etc., and therefore, setting is performed with this point taken into consideration. In specific terms, the hold region A correlates an amount of hysterisis (
As explained above, in a case wherein the target power reverses due to depression of the accelerator by foot when performing speed change control of the continuously variable transmission 4 of belt-type using the target gear ratio “alpha” of the low side, the power and drive force can be changed using only the engine torque by holding the gear ratio of the continuously variable transmission 4 of belt-type, and responsiveness and direct feel with respect to the accelerator operation are improved.
First, when the accelerator opening amount Acc (target power) is changing to a large side, as shown in
As [Positive judgment in Step ST3]→[Step ST6] is sequentially repeated in the flowchart shown in
Next, if the accelerator is subjected to a return operation by foot at a point in time TH2, the accelerator opening amount Acc (target power) reverses towards a small side, and therefore, a target gear ratio “beta”x (not shown) calculated first after that reversal will be equal to or more “high” than the previous actual gear ratio (that is to say, a target gear ratio “beta”H2 calculated immediately after return of the accelerator by foot). At this point in time, or in other words, when the accelerator opening amount Acc (target power) reverses due to a return operation of the accelerator by foot, the gear ratio is held (Step ST5 of
Next, after reversal of the accelerator opening amount Acc (target power), at a point in time where the target gear ratio “alpha” calculated using the up-use map Ma becomes more “high” than the gear ratio held as explained above (a point in time where the judgment of Step ST2 becomes positive), the gear ratio of the continuously variable transmission 4 of belt-type is controlled based on the target gear ratio “alpha” calculated using the up-use map Ma of
As explained above, in a case wherein the target power reverses due to return of the accelerator by foot when performing speed change control of the continuously variable transmission 4 of belt-type using the target gear ratio “beta” of the high side, responsiveness to the accelerator operation can be improved by holding the gear ratio of the continuously variable transmission 4 of belt-type.
Although the target gear ratios “alpha” and “beta” are calculated using the up-use map Ma and the down-use map Mb in the above-explained example, the target gear ratios “alpha” and “beta” can each be calculated using a calculating device.
Although an example of application of the present invention to speed change control of a continuously variable transmission of belt-type was shown in the above explained example, the present invention is not limited to this and, for example, can be applied to speed change control of other continuously variable transmissions such as a traction-type continuously variable transmission, etc.
Although the above example shows an example of application of the present invention in speed change control of a continuously variable transmission of a vehicle whereupon a gasoline engine is mounted, the present invention is not limited to this, and application is possible also in speed change control of a continuously variable transmission of a vehicle whereupon another engine such as a diesel engine, etc. is mounted. Furthermore, the motive power source of the vehicle may, other than an engine (internal combustion engine), be an electric motor or a hybrid-type motive power source comprising an engine and an electric motor.
Note that some symbol characters are described as alphabetical characters as shown below in this specification. Individual alphabetical characters “alpha”, “beta”, and “theta” correspond to respective symbol characters “α”
, “β”
, and “θ”.
It should be noted that without departure from the intention, gist, and principal characteristics thereof, the present invention can have many other embodiments. Accordingly, the above-described embodiments are no more than simple examples and should not be interpreted in a limited manner. The scope of the present invention is set forth by the scope of the patent claims, and the disclosure is in no way binding. In addition, all modifications and changes within a scope equivalent to that of the patent claims are within the scope of the present invention.
Furthermore, this application claims priority based on Patent Application No. 2007-234089, which was filed in Japan on Sep. 10, 2007. Accordingly, all of the content thereof is included in this application by reference.
The present invention can be applied not only to an FF (front-engine, front-drive) type vehicle, but also to an FR (front-engine, rear-drive) type vehicle and a four-wheel drive vehicle.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2007-234089 | Sep 2007 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2008/002371 | 8/29/2008 | WO | 00 | 3/9/2010 |
