WO2005090835A1 - 流体継手を用いた車両用動力伝達装置 - Google Patents
流体継手を用いた車両用動力伝達装置 Download PDFInfo
- Publication number
- WO2005090835A1 WO2005090835A1 PCT/JP2005/005078 JP2005005078W WO2005090835A1 WO 2005090835 A1 WO2005090835 A1 WO 2005090835A1 JP 2005005078 W JP2005005078 W JP 2005005078W WO 2005090835 A1 WO2005090835 A1 WO 2005090835A1
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- WIPO (PCT)
- Prior art keywords
- clutch
- engine
- vehicle
- turbocharger
- speed
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/14—Control of torque converter lock-up clutches
- F16H61/143—Control of torque converter lock-up clutches using electric control means
Definitions
- the present invention includes a fluid coupling (fluid coupling) between an engine and a transmission, and the clutch of the clutch by a vehicle driver when the vehicle starts moving.
- the present invention relates to a vehicle power transmission device that can smoothly start using a slip between a pump and a turbine of a fluid coupling without requiring a complicated operation.
- Power transmission device A typical example is an AT car that uses a power transmission device consisting of a torque converter, which is a fluid transmission device, and a planetary gear mechanism.
- a parallel shaft gear mechanism type transmission similar to that of a so-called manual vehicle is used, and this is combined with an automatic clutch etc.
- a power transmission device that omits clutch operation when switching gears, and is also used in commercial vehicles.
- a power transmission device that uses an electronic control unit and an actuator that operates a transmission instead of a driver operating a shift lever, and automatically switches gears according to the running state of a vehicle.
- a power transmission device with a fluid coupling between the engine and the transmission has been developed.
- a fluid coupling is a type of fluid transmission, unlike a torque converter, it does not have a stator vane and has no torque increasing function, but has a simpler structure than a torque converter. I have.
- With a fluid coupling in place especially in diesel engines with high torque in the low engine speed range, In this case, it is possible to start using the slip between the fluid coupling pump and the turbine. In other words, a delicate clutch operation, such as when starting a manual car, is not required, and a smooth start can be performed.At the same time, torque fluctuations of the engine during idle times are absorbed, and vibration and noise are reduced. You.
- FIG. 2 is a cross-sectional view showing a power transmission device from the crankshaft of the diesel engine to the transmission.
- the fluid coupling 2 is fastened to the rear of the crankshaft 1 and further via a wet multi-plate clutch 3.
- a transmission 4 having a parallel shaft gear mechanism is connected.
- the fluid coupling 2 includes a pump 21 and a turbine 22 that can rotate independently of each other, and the casing 23 is filled with hydraulic oil.
- the pump 21 of the fluid coupling is integrally connected to the crankshaft 1 of the diesel engine by the casing 23, the drive plate 11 and the like. Further, the output shaft 24 of the fluid coupling 2 is connected to the turbine 22, and the input shaft hap part 31 of the wet multiplate clutch 3 is connected to the other end of the output shaft 24 by spline fitting. The output shaft hub 3 2 of the wet multi-plate clutch 3 is also connected to the input shaft 41 of the transmission 4 by spline fitting.
- the pump 21 of the fluid / coupling 2 starts to rotate integrally with the crankshaft 1 and feeds the working oil to the turbine 22.
- the flow rate of hydraulic oil circulating from the pump 21 to the turbine 22 increases, and the torque acting on the turbine 22 increases.
- the wet multi-plate clutch 3 connected to the fluid coupling 2 is in the engaged state by the hydraulic pressure acting on the friction plate except when the vehicle is changing speed.
- the transmission 4 is geared to the starting stage, and the vehicle is stopped by depressing the brake pedal.
- the turbine 22 is also stopped, but with the release of the brake pedal, the turbine 22 starts to rotate, and the vehicle starts to travel via the wet multi-plate clutch 3 and the transmission 4.
- the speed of the diesel engine further increases, and the speed of the turbine 22 increases accordingly.
- the slip of the fluid coupling 2 decreases with the passage of time after traveling, and the rotation speed of the turbine 22 gradually increases while approaching the rotation speed of the pump 21 (the rotation speed of the diesel engine). That is, the ratio of the turbine rotation speed to the pump rotation speed in the fluid coupling approaches 1.
- the slip between the pump 21 and the turbine 22 enables the vehicle to start smoothly.
- the fluid coupling 2 slips, the power transmission efficiency does not reach 100%, and the diesel engine consumes wasteful fuel accordingly. Therefore, when the vehicle starts running and normal driving is possible, the function of the fluid coupling 2 is stopped and the crankshaft 1 and the transmission 4 are directly connected during low-speed driving of, for example, about 20 Km Zh.
- the fluid coupling 2 is provided with a lock-up clutch 25 for fastening the pump 21 and the turbine 22.
- the lock-up clutch 25 is placed opposite to the inner surface of a casing 23 connecting the crankshaft 1 and the pump 21, and is provided on a clutch disk 26 connected to the turbine 22 and on the front side thereof. Friction fading 27.
- the disconnection and engagement of the lock-up clutch 25 are controlled by switching the flow path in which the high-pressure hydraulic oil flows in the casing 23 of the fluid clutch 2, and therefore, the partition wall behind the fluid coupling 2.
- Fig. 3 which is a vertical cross-sectional view of the part 5
- a trochoid pump 51 for pressurizing and sending out hydraulic oil and a flow path switching valve 52 for switching the flow path of hydraulic oil are attached.
- the flow path switching valve 52 is controlled by a lock-up clutch control device 70.
- Hydraulic oil pressurized by the trochoid pump 51 flows into the chamber 28 on the front of the clutch disk 26 from the passage in the center of the output shaft 24 and passes through the narrow gap on the outer periphery of the clutch disk 26.
- the flow path switching valve 52 When the flow is reversed by the flow path switching valve 52, the pressure on the rear side of the clutch disc 26 increases, and the friction fading 27 engages with the inner surface of the casing 23 to engage the lock-up clutch 25.
- the pump 21 of the fluid coupling 2 and the turbine 22 are directly connected.
- the flow passage switching valve 52 is a mouth-up clutch control device that gradually changes the pulse duty ratio using a pi-mouth valve so as to avoid shock due to sudden engagement of the lock-up clutch 25. Is switched by The detailed configuration and control method of the lock-up clutch 25 and the like are described in the aforementioned patent publication.
- the operation of the vehicle power transmission device using the fluid coupling with the lock-up clutch at the time of starting, etc., will be described with reference to FIG. Fig. 8 shows the changes in the engine speed (pump speed of the fluid coupling) and the turbine speed of the vehicle equipped with a naturally aspirated diesel engine with a large displacement since the start.
- the engine When the vehicle is stopped, the engine is rotating at approximately 500 rpm, which is the idling speed, and the turbine speed is zero because the wheels are stopped.
- the driver depresses the accelerator pedal in this state, the engine speed increases and the torque also increases, and the turbine starts rotating and the vehicle starts. Thereafter, as the engine speed increases, the turbine speed also increases, and the vehicle speed gradually increases.
- the turbine speed of the fluid coupling approaches the engine speed, the vehicle speed reaches a predetermined value, and when the engine speed approaches 150 rpm, which is the stall speed described later, the lock-up clutch is connected.
- the pump and turbine are connected (locked up) in response to the command, the two rotate together.
- the speed ratio which is the ratio of the rotation speeds of the turbine and the pump, is near 0.8, and the engagement of the lock-up clutch can be performed smoothly.
- the stall rotation speed of the fluid coupling will be described with reference to FIG.
- the rated output torque curve of the engine intersects with the pump load torque curve. •
- the point of rotation balances at the point, and the engine speed does not increase any further.
- the engine speed in this balanced state is called stall speed.
- the start-up clutch is set so as to be close to this stall speed after the vehicle starts moving.
- the speed ratio usually reaches a value around 0.8, so that the lock-up clutch is smoothly engaged, and there is no further slippage of the fluid coupling, and the transmission efficiency is reduced. Becomes 100%.
- the lock-up clutch is set to engage when the vehicle speed exceeds a specified value and the engine speed approaches the stall speed. Then, the connection of the lock-up clutch and the acceleration of the vehicle after starting can be performed without any trouble.
- a so-called turbo engine equipped with a turbocharger with a turbocharger for the purpose of improving the engine output is combined with a fluid coupling, the number of revolutions rises when the engine is started, and once it becomes almost constant. After that, the number of revolutions gradually increased again, and it turned out that a phenomenon occurs in which the number of revolutions stabilizes again at a higher number of revolutions (see Figure 5). This phenomenon is particularly prominent in engines equipped with a large-capacity turbocharger that has a large increase in engine output, and as if there were multiple stall rotation speeds. Stall. "
- the two-stage stall is caused by the output characteristics of the turbo engine shown by the broken line in FIG.
- the turbocharger cannot exhibit sufficient performance at the time of startup and the pressure (boost) of the air supplied to the engine cylinder is low, so the output torque of the engine is also low. It becomes the characteristic of. If combined with the same fluid coupling as in the case of a naturally aspirated engine, the intersection of the lowermost dashed line and the pump load torque curve (marked with a triangle) will be united, and the engine speed will also peak at the engine speed. (The first stage stall speed in Fig. 5).
- the turbocharger In the first place, the turbocharger is driven by the exhaust gas of the engine, so when the engine with a small amount of exhaust gas is started or when the load is low, its rotation speed is low and it does not perform its function sufficiently.
- the degree of turbocharger function depends on the engine operating conditions. It is closely related to, and can be regarded as a change in the intake pipe boost or the engine speed. Such an operating state of the turbocharger is referred to herein as a “tarpocharger output”.
- Figure 9 shows changes in engine speed, etc. when a lock-up command is issued when the speed ratio is 0.8 as described above, combining a turbo engine that performs high supercharging using a large-capacity turbocharger and a fluid coupling.
- the graph shows that the engine speed fluctuates greatly after the lockup command, and the lock-up clutch is engaged. It shows that the acceleration characteristics before and after the lock-up clutch is engaged are deteriorating.
- the present invention provides a vehicle power transmission device combining a turbo engine and a fluid coupling with a lock-up clutch, which optimizes the timing of fastening the mouth-up clutch after the start ⁇ . With the goal. That is, the present invention provides, as described in claim 1,
- the fluid coupling is connected to an engine equipped with a turbocharger
- the fluid coupling includes a pump coupled to a crankshaft of the engine, a turbine coupled to an output shaft of the fluid coupling, and a lock-up clutch for coupling the pump to the turbine.
- the lock-up clutch control device includes means for detecting an operation state of the turbocharger, and starts engagement of the mouth-up clutch before the turbocharger reaches a high output state.
- the control device for engaging the lock-up clutch includes means for detecting the operating state of the turbocharger, and monitors the operating state. Then, the control device starts the engagement of the lock-up clutch before the turbocharger reaches the high output state, so that the output of the turbocharger increases, the boost increases, and the number of rotations of the engine increases. Before the output torque increases, the fastening of the lock-up clutch can be completed.
- the turbocharger reaches a certain steady operating state after the operation delay period elapses, and the operating state is determined by the engine operating state corresponding to the accelerator pedal depression amount and the like.
- the driver increases the amount of depression of the accelerator pedal, so that after the operation delay period has elapsed, the tar- get charger will be in a high output state close to the operation state at full engine load operation.
- the engine also has a high output and the output torque and the number of revolutions increase, but in the present invention, the lock-up clutch is not engaged at this time. Therefore, it does not take a long time to engage the lock-up clutch, and further, it is possible to suppress a shock at the time of engagement.
- the lock-up clutch When the engine boosts due to the increase in the output of the turbocharger, the lock-up clutch has been fastened and the engine is directly connected to the transmission. The vehicle is accelerated smoothly.
- the operating state of the turbocharger is detected by the means for detecting the rate of change of the engine speed, and the time when the rate of change of the engine speed falls below a predetermined value
- the lock-up clutch control device can start the engagement of the lockup clutch.
- the operating state of the turbocharger is detected by a means for detecting the pressure in the intake pipe of the engine, and when the pressure becomes equal to or higher than a predetermined pressure, the lock-up clutch control device opens. The fastening of the check-up clutch may be started.
- the lock-up clutch can be engaged before the turbocharger reaches a high-power operating condition.
- the lock-up clutch control device detects the speed of the vehicle and controls the engagement of the mouth-up clutch according to the vehicle speed, the engagement of the lock-up clutch is increased. It can be performed reliably.
- FIG. 1 is a schematic diagram of a vehicle power transmission device with a fluid coupling to which the mouth-up clutch control device of the present invention is applied.
- FIG. 2 is a cross-sectional view of a fluid coupling and the like in the vehicle power transmission device.
- FIG. 3 is a sectional view of a partition wall portion of the vehicle power transmission device.
- FIG. 4 is a diagram showing operating characteristics when an engine and a fluid coupling are combined.
- Figure 5 shows the operating characteristics over time of an engine equipped with a turbocharger.
- FIG. 6 is a flowchart showing the operation of the mouth-up clutch control device of the present invention.
- FIG. 7 is a diagram showing the operation of the vehicle provided with the mouth-latch-up clutch control device of the present invention at the time of starting or the like.
- FIG. 8 is a diagram showing the operation of a vehicle equipped with a naturally aspirated engine at the time of starting or the like.
- FIG. 9 is a diagram showing an operation of a vehicle equipped with a turbocharger engine and equipped with a conventional lock-up clutch control device at the time of starting or the like.
- BEST MODE FOR CARRYING OUT THE INVENTION a vehicle power transmission device with a fluid coupling according to the present invention will be described with reference to the drawings.
- FIG. 1 shows a vehicle power including a diesel engine 61 according to the present invention.
- Fig. 3 schematically shows a transmission device.
- the diesel engine 61 is equipped with a turbocharger 62 for supercharging, and the turbocharger 62 is a compressor 621, which compresses the air supplied to the engine cylinder, and a compressor drive connected to this. It has a turbine 62 2.
- the pressure (boost) of the air compressed by the compressor 62 1 rises and is supplied to the cylinder from the intake pipe 63.
- Exhaust gas after combustion in the cylinder flows into the compressor drive turbine 62 2 through the exhaust pipe 64 and rotates the turbine.
- This diesel engine is provided with an EGR passage 65 for recirculating the exhaust gas to the intake pipe 63 to reduce NOX in the exhaust gas.
- the power of the diesel engine 61 is transmitted from the crankshaft 1 to the fluid coupling 2.
- the device constituting the power transmission device for vehicles with a fluid coupling to which the present invention is applied is a conventional device shown in FIG. 2 except that the diesel engine 61 is a turbo engine equipped with a turbocharger 62. It is not something different. That is, a transmission 4 having a parallel shaft gear mechanism is connected to the rear of the fluid coupling 2 via a multi-plate wet clutch 3, which is a clutch that automatically connects and disconnects.
- the pump 21 of the fluid coupling 2 is integrally connected to the crankshaft 1 by a casing 23 and the like, and the turbine 22 rotates integrally with the input shaft of the wet multi-plate clutch 3.
- the wet-type multi-plate clutch 3 is in an engaged state except during shifting, and the turbine 22 is directly connected to the input shaft 41 of the transmission.
- the fluid coupling 2 has a lock-up clutch 25 for connecting the pump 21 and the turbine 22.
- the configuration and control method of the lock-up clutch 25 are the same as those of the conventional device of FIG. 2, and a lock-up clutch control device 70 is provided for controlling the engagement and disengagement of the lock-up clutch 25.
- the flow of hydraulic oil in the casing 23, which is pressure-fed from the trochoid pump 51 is switched by the flow path switching valve 52, and the clutch disc 26 connected to the turbine 22 is formed on the inner surface of the casing 23.
- the lock-up clutch 25 is connected when the flow path is pressed to the side.
- the turbocharger 62 installed in the diesel engine 61 has an operation delay based on the inertia of the compressor 621, the compressor-driven turbine 62, etc. During this period, the output of the turbocharger 62 is low, and the rotation speed of the compressor 621 does not increase sufficiently. Therefore, as shown in FIG. 5, the pressure ratio, which is the ratio between the outlet pressure and the inlet pressure of the compressor 621, hardly increases, and the boost of the intake pipe 63 remains low. Then, during this period, the output of the diesel engine 61 is suppressed, and the rotation speed is suppressed to the stall rotation speed of the first stage.
- the rotation speed of the turbine 22 of the fluid coupling 2 gradually increases, the speed ratio increases, and the vehicle speed of the vehicle also increases accordingly.
- the operation state in which the rotation speed of the turbocharger 62 is low and sufficient performance is not exerted is for a certain short period of time, and thereafter, the boost increases as the output of the turbocharger 62 increases, and the diesel engine 61 The output torque and rotation speed increase. Since the driver depresses the accelerator pedal greatly at the time of starting, the output of the turbocharger 62 becomes a high output state corresponding to the operation at the time of full load of the engine after the operation delay period.
- such an operating state of the turbocharger 62 is detected, and at a time point before the turbocharger 62 reaches the high output state and the output of the diesel engine 62 increases again, the lock-up clutch 25 is activated. Control to generate a connection command signal.
- a rotation speed sensor 71 for detecting the rotation speed of the diesel engine 61 (the rotation speed of the pump 21) is used.
- the speed of the diesel engine 6 1 is the same as the turbocharger 6 2 Before the number of revolutions increases, the number of revolutions reaches a plateau. Thereafter, the number of revolutions of the turbocharger 62 increases with an increase in the output of the turbocharger 62, and the number of revolutions of the diesel engine 61 inevitably increases again.
- the rate of change is calculated from the number of revolutions detected by the revolution number sensor 71, and when the rate of change of the number of revolutions of the diesel engine 61 decreases to a predetermined value after the vehicle starts (point A in FIG. 5).
- the lock-up clutch control device 70 is set to output a connection command signal.
- the turbocharger 62 becomes a high output state, and the connection of the mouth-up clutch 25 is started before the output of the diesel engine 61 increases again.
- the turbocharger 62 is in a high output state and its rotation speed is increased, the boost in the intake pipe 63 is increased.
- the pressure or pressure ratio is detected by the pressure sensor 72 installed in the intake pipe 63, and when this reaches a predetermined pressure ( (Point B in FIG. 5), it is also possible to set so that the connection command signal of the lock-up clutch 25 is output.
- the flow path switching valve 52 When the connection command signal is output from the lock-up clutch control device 70, the flow path switching valve 52 is switched, and the hydraulic oil flows from the working chamber between the pump and the turbine to the chamber 29 behind the clutch disc 26. After that, it flows to the front chamber 28, and the friction fading 27 of the clutch disk 26 is pressed against the inner surface of the casing 23. At this time, the lock-up clutch control device 70 adjusts the switching speed of the flow path switching valve 52 by changing the duty ratio of the control pulse, and controls the hydraulic pressure for pressing the clutch disc 26 appropriately to connect. Prevent shock.
- FIG. 6 shows a flowchart for controlling the engagement of the lock-up clutch according to the present invention.
- the diesel engine 61 starts and the vehicle starts to start, the vehicle speed is detected (S1), and it is determined whether the vehicle speed exceeds, for example, 10 KmZh (S3). This is because when the vehicle speed is too low, the rotation speed of the turbine 22 is very low, and is not suitable for engaging the mouth-up clutch 25.
- the vehicle speed and the rotation speed of the turbine (2 2) have a one-to-one relationship. Therefore, even if the rotation speed of the turbine 22 is detected instead of detecting the vehicle speed. Good. If the vehicle speed has not reached a certain value, the flow ends without outputting the lock-up clutch command.
- the rate of change of the engine speed described below is equal to or less than a predetermined value, the condition for determining the vehicle speed can be omitted in a power transmission device in which the vehicle speed always exceeds a certain value.
- the rate of change of the rotational speed of the diesel engine 61 When the vehicle speed exceeds a certain value, it is determined whether or not the rate of change of the rotational speed of the diesel engine 61 has become a predetermined value or less (S4). For this reason, the rotational speed is always detected by the rotational speed sensor, and the calculation of the rate of change is executed (S2). If the rate of change is equal to or greater than the predetermined value, the flow ends because it is not yet time to close the mouth clutch. When the predetermined value is reached, it is determined that the appropriate timing has been reached, and the mouth-up clutch control device 70 outputs a command to engage the lock-up clutch 25, and starts the duty ratio control for engagement (S5 S6).
- the present invention relates to a vehicle power transmission device in which a turbo engine and a fluid coupling with a lock-up clutch are combined, comprising: means for detecting an operating state of a turbocharger; While monitoring the operation status, the timing of lock-up clutch engagement after starting is optimized.
- the present invention can be used for vehicles having such a power transmission device, and is applicable not only to diesel engines but also to turbocharged gasoline engines. It is also apparent that the present invention can be applied to a power transmission device without a clutch such as a wet multi-plate clutch behind the fluid coupling.
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Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2005224533A AU2005224533B2 (en) | 2004-03-18 | 2005-03-15 | Vehicle power transmission device using a fluid coupling |
US10/592,357 US7534192B2 (en) | 2004-03-18 | 2005-03-15 | Vehicle power transmission device using a fluid coupling |
EP05721228A EP1729039B1 (en) | 2004-03-18 | 2005-03-15 | Power transmitter for vehicles employing fluid coupling |
DE602005014754T DE602005014754D1 (de) | 2004-03-18 | 2005-03-15 | Leistungsübertrager für eine flüssigkeitskupplung einsetzende fahrzeuge |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-078522 | 2004-03-18 | ||
JP2004078522A JP3832474B2 (ja) | 2004-03-18 | 2004-03-18 | 流体継手を用いた車両用動力伝達装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005090835A1 true WO2005090835A1 (ja) | 2005-09-29 |
Family
ID=34993779
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/005078 WO2005090835A1 (ja) | 2004-03-18 | 2005-03-15 | 流体継手を用いた車両用動力伝達装置 |
Country Status (9)
Country | Link |
---|---|
US (1) | US7534192B2 (ja) |
EP (1) | EP1729039B1 (ja) |
JP (1) | JP3832474B2 (ja) |
CN (1) | CN100427810C (ja) |
AU (1) | AU2005224533B2 (ja) |
DE (1) | DE602005014754D1 (ja) |
ES (1) | ES2327856T3 (ja) |
PT (1) | PT1729039E (ja) |
WO (1) | WO2005090835A1 (ja) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4211844B2 (ja) | 2006-11-24 | 2009-01-21 | いすゞ自動車株式会社 | 車両のロックアップクラッチ制御装置 |
FR2955818B1 (fr) * | 2010-01-29 | 2012-03-09 | Peugeot Citroen Automobiles Sa | Procede de changement de rapport ameliore pour vehicule a moteur thermique muni d'un turbocompresseur |
DE102010028069A1 (de) * | 2010-04-22 | 2011-10-27 | Zf Friedrichshafen Ag | Verfahren zur Schaltsteuerung eines Kraftfahrzeugs |
JP5155357B2 (ja) | 2010-04-26 | 2013-03-06 | ジヤトコ株式会社 | ロックアップクラッチの制御装置 |
CN101856970B (zh) * | 2010-06-13 | 2013-05-08 | 程秀生 | 重型及商用汽车液力辅助起步与液压辅助制动装置 |
CN102562273B (zh) * | 2012-02-13 | 2014-01-08 | 清华大学 | 具有可变几何增压涡轮的涡轮复合装置及其发动机系统 |
CN108644341A (zh) * | 2018-06-29 | 2018-10-12 | 吉林大学 | 一种基于速度识别轨道工程车多液力传动箱及其控制方法 |
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JPS62228750A (ja) * | 1986-03-27 | 1987-10-07 | Mazda Motor Corp | 自動変速機の制御装置 |
JPS6315358U (ja) * | 1986-07-17 | 1988-02-01 | ||
JPH0329762U (ja) * | 1989-07-31 | 1991-03-25 | ||
JPH09144866A (ja) * | 1995-11-27 | 1997-06-03 | Toyota Motor Corp | 過給機を有する車両の油圧制御装置 |
JP2000027987A (ja) * | 1998-07-10 | 2000-01-25 | Hino Motors Ltd | 車両用自動変速機制御装置 |
JP2002022000A (ja) * | 2000-07-11 | 2002-01-23 | Toyota Motor Corp | 車両用ロックアップクラッチの制御装置 |
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US4510747A (en) | 1980-12-12 | 1985-04-16 | Daihatsu Motor Company Limited | Lockup control device for a torque converter |
JPS6198627A (ja) * | 1984-10-17 | 1986-05-16 | Mazda Motor Corp | 自動車のパワ−ユニツト |
JPH07108630B2 (ja) | 1987-07-31 | 1995-11-22 | マツダ株式会社 | 自動変速機付車両の制御装置 |
JP4207352B2 (ja) | 2000-02-28 | 2009-01-14 | いすゞ自動車株式会社 | 動力伝達装置 |
US6607467B2 (en) * | 2000-07-11 | 2003-08-19 | Toyota Jidosha Kabushiki Kaisha | Apparatus for controlling vehicle drive system including engine with turbocharger, and lock-up clutch |
JP3756765B2 (ja) * | 2001-01-26 | 2006-03-15 | アスモ株式会社 | 車両用ミラー駆動装置及びリンク機構 |
-
2004
- 2004-03-18 JP JP2004078522A patent/JP3832474B2/ja not_active Expired - Fee Related
-
2005
- 2005-03-15 EP EP05721228A patent/EP1729039B1/en not_active Not-in-force
- 2005-03-15 US US10/592,357 patent/US7534192B2/en not_active Expired - Fee Related
- 2005-03-15 PT PT05721228T patent/PT1729039E/pt unknown
- 2005-03-15 WO PCT/JP2005/005078 patent/WO2005090835A1/ja not_active Application Discontinuation
- 2005-03-15 DE DE602005014754T patent/DE602005014754D1/de active Active
- 2005-03-15 CN CNB2005800087042A patent/CN100427810C/zh not_active Expired - Fee Related
- 2005-03-15 ES ES05721228T patent/ES2327856T3/es active Active
- 2005-03-15 AU AU2005224533A patent/AU2005224533B2/en not_active Ceased
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62228750A (ja) * | 1986-03-27 | 1987-10-07 | Mazda Motor Corp | 自動変速機の制御装置 |
JPS6315358U (ja) * | 1986-07-17 | 1988-02-01 | ||
JPH0329762U (ja) * | 1989-07-31 | 1991-03-25 | ||
JPH09144866A (ja) * | 1995-11-27 | 1997-06-03 | Toyota Motor Corp | 過給機を有する車両の油圧制御装置 |
JP2000027987A (ja) * | 1998-07-10 | 2000-01-25 | Hino Motors Ltd | 車両用自動変速機制御装置 |
JP2002022000A (ja) * | 2000-07-11 | 2002-01-23 | Toyota Motor Corp | 車両用ロックアップクラッチの制御装置 |
Also Published As
Publication number | Publication date |
---|---|
JP3832474B2 (ja) | 2006-10-11 |
PT1729039E (pt) | 2009-09-01 |
US7534192B2 (en) | 2009-05-19 |
JP2005265050A (ja) | 2005-09-29 |
US20070207893A1 (en) | 2007-09-06 |
AU2005224533A1 (en) | 2005-09-29 |
ES2327856T3 (es) | 2009-11-04 |
EP1729039A1 (en) | 2006-12-06 |
AU2005224533B2 (en) | 2008-02-28 |
CN1934378A (zh) | 2007-03-21 |
CN100427810C (zh) | 2008-10-22 |
DE602005014754D1 (de) | 2009-07-16 |
EP1729039B1 (en) | 2009-06-03 |
EP1729039A4 (en) | 2007-11-14 |
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