WO2016084588A1 - 自動変速機 - Google Patents
自動変速機 Download PDFInfo
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- WO2016084588A1 WO2016084588A1 PCT/JP2015/081450 JP2015081450W WO2016084588A1 WO 2016084588 A1 WO2016084588 A1 WO 2016084588A1 JP 2015081450 W JP2015081450 W JP 2015081450W WO 2016084588 A1 WO2016084588 A1 WO 2016084588A1
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- WIPO (PCT)
- Prior art keywords
- pressure
- hydraulic pressure
- rotational speed
- oil
- transmission device
- Prior art date
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- 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
- F16H61/38—Control of exclusively fluid gearing
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- 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
- F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
- F16H39/04—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit
- F16H39/42—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motor and pump combined in one unit pump and motor being of different types
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- 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
- F16H61/0021—Generation or control of line pressure
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- 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
- F16H61/02—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 characterised by the signals used
- F16H61/0262—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 characterised by the signals used the signals being hydraulic
- F16H61/0265—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 characterised by the signals used the signals being hydraulic for gearshift control, e.g. control functions for performing shifting or generation of shift signals
- F16H61/0267—Layout of hydraulic control circuits, e.g. arrangement of valves
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- 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
- F16H61/02—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 characterised by the signals used
- F16H61/0262—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 characterised by the signals used the signals being hydraulic
- F16H61/0276—Elements specially adapted for hydraulic control units, e.g. valves
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- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/48—Control of exclusively fluid gearing hydrodynamic
- F16H61/64—Control of exclusively fluid gearing hydrodynamic controlled by changing the amount of liquid in the working circuit
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- 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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H2059/366—Engine or motor speed
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- 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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H59/38—Inputs being a function of speed of gearing elements
- F16H2059/385—Turbine speed
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- 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
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/1232—Bringing the control into a predefined state, e.g. giving priority to particular actuators or gear ratios
- F16H2061/1236—Bringing the control into a predefined state, e.g. giving priority to particular actuators or gear ratios using fail priority valves
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- 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
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/124—Limiting the input power, torque or speed
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- 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
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/1252—Fail safe valves
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- 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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/36—Inputs being a function of speed
- F16H59/46—Inputs being a function of speed dependent on a comparison between speeds
Definitions
- This technology relates to an automatic transmission mounted on a vehicle or the like, and more particularly to an automatic transmission including a fluid transmission device that transmits fluid by oil filled with rotation of a drive source.
- Some automatic transmissions mounted on vehicles and the like include a fluid transmission device such as a torque converter that fluidly transmits engine rotation using filled oil as a working fluid.
- a fluid transmission device such as a torque converter that fluidly transmits engine rotation using filled oil as a working fluid.
- the rotation of the input shaft of the automatic transmission mechanism transmission
- the brake is stopped by the brake.
- the engine rotation is transmitted to the input shaft of the automatic transmission mechanism to start the vehicle. It has been.
- a lockup clutch is used in the state where there is no or little oil in a fluid transmission device. Since it tries to engage, lubrication and cooling are not sufficient, and durability may be affected. In addition, it is necessary to slip the lock-up clutch so that the engine does not stop when starting, but even if the slip state of the lock-up clutch is controlled by the differential pressure inside the fluid transmission, the oil inside the fluid transmission Since it is difficult to accurately grasp the amount, the controllability is not improved, and there is a possibility that an engagement shock occurs when the vehicle starts.
- This automatic transmission A fluid transmission device that fluidly transmits the rotation of the drive source by filled oil; A speed change mechanism that shifts and outputs the output rotation of the fluid transmission device; A hydraulic control device comprising: a circulating hydraulic pressure regulating valve that regulates hydraulic pressure discharged from an oil pump to a circulating hydraulic pressure that circulates through the fluid transmission device; and a pressure regulating solenoid valve that supplies a signal pressure to the circulating hydraulic pressure regulating valve
- a drive source rotation acquisition unit that acquires a rotation speed of the drive source
- a fluid transmission device rotation acquisition unit that acquires an output rotation speed of the fluid transmission device, the output rotation speed of the fluid transmission device and the drive
- the pressure regulating solenoid valve is controlled so that the circulating hydraulic pressure becomes the first circulating hydraulic pressure, and the output rotational speed of the fluid transmission device and the When the rotational speed difference from the rotational speed of the drive source is larger than a predetermined rotational speed
- the fluid transmission device when the oil in the fluid transmission device is drained, the fluid transmission device can be quickly filled with oil by increasing the circulating oil pressure, so without relying on a mechanical oil leakage prevention structure, Further, it is possible to prevent the occurrence of the lost driving force at the time of starting after the drive source has been stopped for a long time without using a lock-up clutch.
- the block diagram which shows this automatic transmission The hydraulic circuit diagram which shows a part of hydraulic control apparatus of this automatic transmission.
- the flowchart which shows the control by the control part of this automatic transmission.
- the figure which shows an example of a command value map.
- the time chart which shows the relationship between the engine speed at the time of engine starting when a torque converter is filled with oil, and turbine speed.
- the time chart which shows the relationship between the engine speed at the time of engine starting at the time of oil having drained from the torque converter, and turbine speed.
- control unit 1 of the automatic transmission 3 a control device 1 of the automatic transmission 3
- the automatic transmission 3 shifts the output rotation of the torque converter (fluid transmission device) 4 connected to the engine (drive source) 2 and the torque converter 4 to a wheel (not shown).
- Automatic transmission mechanism (transmission mechanism) 5 to be output in this manner, the circulating hydraulic pressure of these torque converters 4, the operating hydraulic pressure supplied to friction engagement elements (clutch and brake) (not shown) of the automatic transmission mechanism 5, and the automatic transmission mechanism 5
- a hydraulic control device 6 that hydraulically controls a lubricating hydraulic pressure for supplying lubricating oil to the vehicle, and a control unit (ECU) 1 that will be described later in detail.
- the torque converter 4 includes a pump impeller 4a that is drivingly connected to the engine 2, a turbine runner 4b that transmits the rotation of the pump impeller 4a via a working fluid (oil), and the pump
- the stator 4c is interposed between the impeller 4a and the turbine runner 4b and the reverse rotation is restricted by the one-way clutch F.
- the turbine runner 4b is driven by an input shaft (not shown) of the automatic transmission mechanism 5. It is connected.
- the torque converter 4 is provided with a lock-up clutch 7, and when the lock-up clutch 7 is engaged, the rotation of the engine 2 is transmitted to the input shaft of the automatic transmission mechanism 5 as it is.
- an oil pump 21 that is drivingly connected to the engine 2 via a pump impeller 4a of the torque converter 4 and driven in conjunction with the engine 2 is provided. Is provided.
- the torque converter 4 configured in this manner is fluid-transmitted by the oil filled with the rotation of the engine 2 and transmits a driving force to an input shaft (not shown) of the automatic transmission mechanism 5.
- the automatic transmission mechanism 5 is composed of, for example, a multi-stage system, and forms a transmission path having a different gear ratio according to the engagement state of a plurality of friction engagement elements according to each shift stage, thereby shifting the rotation input to the input shaft. And output to the wheels via a differential device or the like.
- the automatic transmission mechanism 5 is not limited to a multistage type (stepped type) but may be a continuously variable type using a belt type continuously variable transmission, a toroidal type continuously variable transmission, or the like.
- the control unit (ECU) 1 includes a throttle opening sensor 81 (which may be an accelerator opening sensor that detects the accelerator opening) that detects the opening of a slot valve (not shown), and the turbine runner.
- a turbine rotational speed sensor 82 for detecting a rotational speed (turbine rotational speed Nt) of 4b (or an input shaft of the automatic transmission mechanism) is connected, and an engine rotational speed (engine rotational speed Ne) from the engine 2 to the engine 2 is connected.
- This signal can be input, and is connected so as to be able to transmit a command signal to the hydraulic control device 6 that hydraulically controls the automatic transmission mechanism 5 described above.
- the control unit 1 includes a line pressure control unit (circulation hydraulic pressure increase unit) 11, an oil shortage determination unit 12, a command value map 13, an engine rotation speed acquisition unit as units for which a program recorded in a ROM or the like functions. (Drive source rotation acquisition unit) 14 and turbine rotation speed acquisition means (fluid transmission device rotation acquisition unit) 15 are provided.
- the engine speed Ne may be detected by providing a sensor for detecting the rotational speed of the input member of the pump impeller 4a or the automatic transmission 3.
- the hydraulic control device 6 includes a strainer 22, an oil pump 21, a primary regulator valve 24, a secondary regulator valve 25, a manual shift valve 23, a solenoid valve SL, a lock-up relay valve 26, an oil cooler (COOLER). 33, a lubricating oil passage (LUBE) 34, and the like.
- the hydraulic control device 6 includes various valves and oil passages for supplying hydraulic pressure to the hydraulic servos of the clutches and brakes of the transmission mechanism in addition to the portions shown in FIG. In order to simplify the description, the description is omitted.
- reference numeral SLT shown in Figure 2 there is shown by omitting the linear solenoid valve (pressure regulating solenoid valve) SLT for pressure regulating the line pressure P L, the throttle opening degree by the linear solenoid valve SLT It shows that the SLT pressure P SLT regulated based on the output is outputted.
- reference numeral 32 shown in FIG. 2 there is shown by omitting the modulator valve 32, that is the line pressure P L and outputs the modulator pressure P MOD that by regulating the constant pressure by the modulator valve 32 Is shown.
- the hydraulic control device 6 includes an oil pump 21 that is driven in conjunction with the rotation of the engine 2, and generates oil pressure by sucking oil from an oil pan (not shown) through a strainer 22 by the oil pump 21. I am letting.
- the hydraulic pressure generated by the oil pump 21 is output from the output port 21a to the oil passages a1, a2, a3, a4, a5, a6, a7, and a line that will be described later in detail by the primary regulator valve 24 described later in detail. the pressure is adjusted to the pressure P L.
- Manual shift valve 23 has a spool 23p is driven in conjunction with the shift lever not shown, an input port 23a of the line pressure P L to be described later is input, the spool 23p is forward range (D-range, 2-range, a forward range pressure output port 23b to output when driven at the position of the L range) the line pressure P L as a forward range pressure P D, when the spool 23p is driven to the position of the reverse range (R range) It has a reverse range pressure output port 23c for outputting the line pressure P L as a reverse range pressure P R, to.
- D-range 2-range
- a forward range pressure output port 23b to output when driven at the position of the L range
- the line pressure P L as a forward range pressure P D
- R range reverse range
- It has a reverse range pressure output port 23c for outputting the line pressure P L as a reverse range pressure P R, to.
- the reverse range pressure P R that is output from the rear proceeds range pressure output port 23c to R-range is supplied as a source pressure to the hydraulic servo of the friction engagement elements forming the reverse gear via the oil passage not shown in FIG. 2 A reverse gear is formed.
- the forward range pressure PD output from the forward range pressure output port 23b in the D range is output to an oil chamber 24b of the primary regulator valve 24 described later via the oil passages k1 and k2, and the oil passage. From k3, it is supplied as an original pressure to each linear solenoid valve (not shown) via an oil passage omitted in FIG. 2, and finally supplied to a hydraulic servo of a friction engagement element that forms each forward stage. An advance stage is formed.
- the check valve 42 when the neutral range (N range) or a parking range (P range), when the forward range pressure P D is discharged from the drain port EX of the manual shift valve 23 is equal to or less than the predetermined pressure It is configured to close, and air is prevented from entering the manual shift valve 23, the oil passages k1, k2, k3, and the like.
- the primary regulator valve (line pressure regulating valve) 24 includes a spool 24p, a spring 24s that urges the spool 24p upward in the drawing, and a plug 24r, and an oil chamber 24a above the spool 24p. And an oil chamber 24f below the plug 24r, an oil chamber 24b formed by the difference in land diameter of the spool 24p, a discharge port 24c, a pressure adjusting port 24d, and a discharge pressure output port 24e. ing.
- the SLT pressure P SLT is input to the oil chamber 24f through the oil passages j1 and j2 from the linear solenoid valve SLT, and the line pressure P L described later in detail is supplied to the oil chamber 24a. , A6, and input as feedback pressure. Further, the oil chamber 24b as described above, the forward range pressure P D is input via the oil passage k1, k2 at the time of the forward range.
- the urging force of the spring 24s and the SLT pressure P SLT act on the spool 24p of the primary regulator valve 24 through the plug 24r in opposition to the feedback pressure. That is, the position of the spool 24p is mainly SLT. It is controlled by the magnitude of the pressure P SLT .
- the pressure adjusting port 24d and the discharge port 24c communicate with each other, and the spool 24p is controlled to move to the upper side in the figure based on the SLT pressure P SLT .
- the communication amount (throttle amount) between the pressure adjustment port 24d and the discharge port 24c is reduced (blocked), and the communication amount (throttle amount) between the pressure adjustment port 24d and the exhaust pressure output port 24e.
- Is squeezed (blocked). That is, the spool 24p is controlled to move upward according to the magnitude of the SLT pressure P SLT input to the oil chamber 24f, and the amount of hydraulic pressure discharged from the discharge port 24c is adjusted to adjust the pressure adjustment port 24d. pressurized hydraulic of tone, whereby the oil passage a1, a2, a3, a4, a5, a6, a7 pressure of is pressure regulated as a line pressure P L corresponding to the throttle opening.
- the input torque input from the engine 2 to the automatic transmission 3 is calculated from the speed ratio (Ne / Nt) between the engine speed Ne and the turbine speed Nt, and is determined according to this input torque.
- the line pressure P L is defined as a reference line pressure, details the line pressure P L is increased by the line pressure increase control to be described later, it will be raised to be higher than the reference line pressure.
- the forward range pressure P D to the forward range when the oil chamber 24b as described above is input, and urges the spool 24p downward, i.e. SLT gain of pressure P SLT line pressure for P L (O ratio) Will be lowered. That is, in the time of reverse running, because the torque capacity of the clutch C-3 and brake B-3 required is large, but it is required to increase the gain of the line pressure P L for SLT pressure P SLT, one forward in the time of traveling, even down gain of the line pressure P L for SLT pressure P SLT is, the clutch C-1, the clutch C-2, a sufficient torque capacity as a hydraulic pressure supplied to the hydraulic servo of the brake B-1
- the line pressure P L can be ensured, that is, the line pressure P L output according to the throttle opening is suppressed low, and the increase in the useless line pressure P L is suppressed, thereby improving the fuel efficiency of the vehicle. Is possible.
- the hydraulic pressure discharged from the discharge port 24c is returned to the port 21b of the oil pump 21 through the oil passages d2 and d3 and becomes the original pressure of the oil pump 21, so that the oil pump 21 is necessary as a result.
- the driving force is reduced, it is possible to prevent wasteful energy consumption, and it is possible to contribute to the improvement of the fuel consumption of the vehicle including the automatic transmission 3.
- the line pressure P L is also supplied to the modulator valve 32 through an oil passage (not shown), and the modulator valve 32 can maintain the hydraulic pressure as it is if the line pressure P L is equal to or lower than a predetermined pressure.
- output as the modulator pressure P MOD when the line pressure P L is equal to or greater than the predetermined pressure, outputs a hydraulic pressure by regulating the constant pressure as the modulator pressure P MOD.
- the check valve 41 which is connected via an oil passage a2 to the oil pump 21 is a valve line pressure P L is opened when excessively increased, the line pressure in order to protect the hydraulic control device 6 to drain the line pressure P L when the P L is equal to or greater than a predetermined pressure.
- the secondary regulator valve (circulation hydraulic pressure regulating valve) 25 includes a spool 25p and a spring 25s that urges the spool 25p upward in the drawing, and an oil chamber 25a above the spool 25p.
- An oil chamber 25b, a discharge port 25c, a pressure adjustment port 25d, and a discharge pressure output port 25e are provided below 25p.
- the aforementioned oil chamber 25b, SLT pressure P SLT through an oil passage j1, j3 from the aforementioned linear solenoid valve SLT is input also to the oil chamber 25a, the secondary pressure P SEC is oil passage b2, b4, b5 Is input as feedback pressure.
- the urging force of the spring 25s and the SLT pressure P SLT act on the spool 25p of the secondary regulator valve 25 in opposition to the feedback pressure. That is, the position of the spool 25p is mainly the magnitude of the SLT pressure P SLT . It is controlled by When the spool 25p is in the lower state in the figure, the pressure regulating port 25d and the discharge port 25c communicate with each other, and the spool 25p is controlled to move to the upper side in the figure based on the SLT pressure P SLT . Then, the communication amount (throttle amount) between the pressure adjustment port 25d and the discharge port 25c is reduced (blocked), and the communication amount (throttle amount) between the pressure adjustment port 25d and the exhaust pressure output port 25e.
- the spool 25p is controlled to move upward according to the magnitude of the SLT pressure P SLT input to the oil chamber 25f, and the hydraulic pressure discharged from the discharge port 25c is adjusted to adjust the pressure adjustment port 25d.
- pressurized hydraulic of tone whereby the oil passage b1, b2, b3, b4, b5, b6, b7 of the hydraulic pressure is pressure secondary pressure regulated as (circulating oil pressure) P SEC in accordance with the throttle opening.
- the oil pump 21 generates a hydraulic pressure in conjunction with the engine speed, the line pressure P L becomes a normal pressure adjusting region, and the exhaust pressure of the line pressure P L is output from the primary regulator valve 24.
- the feedback pressure of the oil chamber 25a of the secondary regulator valve 25 overcomes the urging force of the spring 25s, and the pressure regulating port 25d and the exhaust pressure output port 25e begin to communicate (secondary cracks).
- the secondary pressure P SEC is discharged from the discharge pressure output port 25e when the secondary pressure P SEC is reached.
- Exhaust pressure of the secondary pressure P SEC is output via the oil path c1, c2 to the lubricating oil passage (LUBE) 34 that communicates with the automatic speed change mechanism 5, that is, lubrication pressure of the lubricating oil.
- LUBE lubricating oil passage
- the oil pressure discharged from the discharge port 25c is returned to the port 21b of the oil pump 21 through the oil passages d1 and d3 and becomes the original pressure of the oil pump 21 as in the case of the primary regulator valve 24.
- the required driving force of the oil pump 21 is reduced, it is possible to prevent wasteful energy consumption, and it is possible to contribute to the improvement of fuel consumption of the vehicle including the automatic transmission 3.
- the solenoid valve SL (for example, normally closed) has an input port SLa and an output port SLb, and the modulator pressure P MOD regulated by the modulator valve 32 is input to the input port SLa.
- the solenoid valve SL When the solenoid valve SL is in an OFF state (non-energized state), the input port SLa and the output port SLb are shut off.
- the solenoid valve SL When the solenoid valve SL is turned on (energized state) based on a signal from the control unit 1, The output port SLb communicates, and the modulator pressure P MOD input to the input port SLa is output as it is as the signal pressure P SL from the output port SLb, that is, based on the signal from the control unit 1, the signal pressure P SL is output. Switches the output state.
- the signal pressure P SL output from the output port SLb is input to an oil chamber 26a of a lockup relay valve 26 described later via an oil passage e1.
- the solenoid valve SL has been described as a so-called normally closed type in which the input port SLa and the output port SLb are shut off when not energized. Conversely, the input port SLa and the output port SLb communicate with each other when not energized. In this case, the signal pressure PS1 is not output in the energized state.
- the lockup relay valve (switching valve) 26 includes a spool 26p and a spring 26s that urges the spool 26p upward in the drawing, and an oil chamber 26a, an input port 26b, and the spool 26p. , A port 26c, an output port 26d, an input port 26e, a port 26f, a port 26g, and a discharge port 26h.
- the aforementioned oil chamber 26a, through the oil passage e1 is connected to the output port SLb of the solenoid valve SL, when the solenoid valve SL from the signal pressure P SL is outputted, the signal pressure P SL is input
- the lock-up relay valve 26 is in the position indicated by the left half in the figure (hereinafter referred to as “left half position”) when the signal pressure P SL is not output from the solenoid valve SL, and the solenoid valve SL.
- the position indicated by the right half in the figure hereinafter referred to as “right half position” is obtained, that is, the lockup relay valve 26 is switched based on the input state of the signal pressure P SL. .
- the input port 26b and the port 26c communicate with each other
- the port 26g and the output port 26d communicate with each other
- the input port 26e and the port 26f communicate with each other.
- the port 26c and the output port 26d communicate with each other
- the input port 26e and the port 26g communicate with each other
- the port 26f and the discharge port 26h communicate with each other
- the input port 26b is blocked by the spool 26p.
- the solenoid valve SL when the solenoid valve SL is in an OFF state based on a command from the control unit 1, no hydraulic pressure is input to the oil chamber 26a, and the spool 26p is in the left half position based on the urging force of the spring 26s. Then, the secondary pressure P SEC via the oil passage b2, b3 are input to the input port 26e is output from the port 26f, the torque converter 4 through an oil passage g1 ports (L-UP ⁇ OFF port) 4e In other words, the secondary pressure P SEC is supplied into the torque converter 4 as a circulating oil pressure for circulating the oil in the torque converter 4.
- the oil supplied into the torque converter 4 is discharged from the port (L-UP / ON port) 4d, input to the port 26g of the lockup relay valve 26 via the oil passage f1, and further output from the output port 26d. Then, the oil is input to an oil cooler (COOLER) 33 through an oil passage h1. The oil input to the oil cooler 33 is cooled by the oil cooler 33, discharged to an oil pan (not shown), and again sucked into the oil pump 21 through the strainer 22.
- COOLER oil cooler
- the secondary pressure PSEC When the secondary pressure PSEC is thus input from the port 4e of the torque converter 4 and discharged from the port 4d, the piston 7a of the lockup clutch 7 is separated from the front cover 4f, that is, the lockup clutch 7 is released. Off. That is, in this state, the secondary pressure PSEC is supplied as the circulating oil pressure of the torque converter 4 and is not supplied as the lockup engagement pressure, but the supply of the lockup engagement pressure is turned off.
- the input port is connected via the oil passages b2, b4, b6, the orifice 51, the check valve 43, and the oil passage b7.
- secondary pressure P SEC that is input to the 26b is supplied to the lubricating oil passage 34 from the port 26c via the oil passage c3, c2.
- the check valve 43 interposed between the oil passage b6 and the oil passage b7 are non-return to prevent the discharge pressure of the secondary pressure P SEC is flowing back to the oil passage b6 via the oil passage c1, c3, b7 It is provided as a valve.
- the solenoid valve SL on the basis of a command of the control unit 1 is in the ON state, the lock-up relay valve 26, the signal pressure P SL is input to the oil chamber 26a, against the biasing force of the spring 26s Thus, the spool 26p is in the right half position. Then, the secondary pressure P SEC via the oil passage b2, b3 are input to the input port 26e is output from the port 26 g, it is supplied to the port 4d of the torque converter 4 via the oil passage f1, i.e. the torque converter 4 the secondary pressure P SEC is supplied as lockup apply pressure to.
- the secondary pressure PSEC is discharged from the port 4e in this way, the hydraulic pressure in the space between the piston 7a of the lockup clutch 7 and the front cover 4f is reduced, and the piston 7a becomes the secondary pressure in the torque converter 4.
- the front cover 4f is pressed and driven, that is, the lockup clutch 7 is engaged.
- the secondary pressure P SEC is supplied to the torque converter 4 as the lock-up engagement pressure, is a state of turning on the supply of the lock-up engagement pressure.
- control by the control unit 1 of the automatic transmission 3 will be described with reference to FIGS. 3 to 5 with reference to FIG.
- a start switch READY switch
- the line pressure increase control (circulation hydraulic pressure increase control) by the control unit 1 described below will be described as being executed after the engine 2 is started and while the vehicle is stopped (vehicle speed is 0).
- the line pressure increase control is started immediately after the engine 2 is started by the driver, the line pressure increase control is performed even when the vehicle is started by switching the shift range to the D (drive) range. Can be executed as is.
- the automatic transmission 3 changes from the gear position at the time of starting (for example, the first forward speed) to the next gear position, that is, the gear ratio changes from the gear ratio at the time of starting.
- the gear ratio changes from the gear ratio at the time of starting.
- the engine rotation speed acquisition unit 14 receives an engine rotation speed signal from the engine 2 (engine control unit). While acquiring the engine rotational speed Ne, the turbine rotational speed acquisition means 15 acquires the turbine rotational speed Nt by receiving a turbine rotational speed signal from the turbine rotational speed sensor 82 (S2).
- a description is given of receiving an engine rotation speed signal from the engine 2.
- an input shaft (not shown) of the automatic transmission 3 and a sensor for detecting the rotation speed of the pump impeller 4a are provided. Then, the engine speed Ne may be acquired from the sensor.
- the oil shortage determination means 12 calculates a rotational speed difference (rotational speed difference) (Ne ⁇ Nt) between the acquired engine rotational speed Ne and the turbine rotational speed Nt, and the rotational speed difference is calculated as a predetermined rotational speed (predetermined rotational speed). It is determined whether or not the rotation speed is greater than ⁇ N (S3).
- rotational speed difference rotational speed difference
- S3 predetermined rotational speed
- the engine 2 is temporarily increased from the idling speed by adding the torque by the ignition to the torque by the starter, and then immediately stabilizes at the idling speed.
- the turbine rotational speed Nt is stabilized at a rotational speed slightly lower than the engine rotational speed Ne, which is the idle rotational speed, due to drag resistance of the automatic transmission mechanism 5 and the like.
- a rotational speed difference (Ne ⁇ Nt) between the engine rotational speed Ne and the turbine rotational speed Nt. ) Does not exceed the predetermined rotational speed ⁇ N and is equal to or lower than the predetermined rotational speed ⁇ N (No in S3), that is, the oil shortage determining means 12 does not determine whether the torque converter 4 has lost oil. Therefore, the line pressure control means 11 in accordance with the command value map 13 shown in FIG. 4, so that the normal line pressure P L, that is determined based on the input torque as described above oil pressure command value of the linear solenoid valve SLT (S6) and repeat this control (return).
- the line pressure control means 11 indicates that the turbine rotational speed Nt is different from the predetermined rotational speed ⁇ N regardless of the engine rotational speed Ne as in the command value map 13 shown in FIG. If it is not open, A [pa] is selected as the hydraulic pressure command value, and the line pressure P L is set to A [A] as the minimum line pressure P L required for the hydraulic control device 6 when the engine 2 is idle. pa] to the linear solenoid valve SLT.
- the exhaust pressure of the line pressure P L is supplied from the exhaust pressure output port 24e of the primary regulator valve 24 to the pressure adjustment port 25d of the secondary regulator valve 25 in a state controlled to be the normal line pressure P L.
- the secondary pressure Psec is regulated by the secondary regulator valve 25 in accordance with the SLT pressure P SLT , and this becomes the normal circulating hydraulic pressure (first circulating hydraulic pressure) supplied to the torque converter 4.
- This normal circulating hydraulic pressure is designed to be a hydraulic pressure that enables transmission of power to the torque converter 4.
- the line pressure control means 11 starts the line pressure increase control, commanding the hydraulic pressure command value to the linear solenoid valve SLT as in accordance with the command value map 13 shown in FIG. 4, the line pressure P L rises above normal (S5).
- the solenoid valve SL is controlled to be off, the lockup relay valve 26 is in the left half position, and the secondary pressure PSEC is supplied as the circulating oil pressure (not supplied as the lockup engagement pressure). is there.
- the line pressure control means 11 is normal when the engine speed Ne is 1100 [rpm] and the turbine speed Nt is 200 [rpm], as in the command value map 13 shown in FIG.
- a hydraulic pressure command value obtained by adding 600 [pa] to the hydraulic pressure command value A [pa] is selected, the engine speed Ne is 2100 [rpm] and the turbine speed Nt is 200 [rpm].
- Selects a hydraulic pressure command value obtained by adding 850 [pa] to the normal hydraulic pressure command value A [pa] the engine speed Ne is, for example, 2100 [rpm]
- the turbine speed Nt is 1100 [rpm].
- a hydraulic pressure command value obtained by adding 550 [pa] to the normal hydraulic pressure command value A [pa] is selected.
- the line pressure control means 11 increases the line pressure P as the rotational speed difference (Nt ⁇ Ne) from the engine rotational speed Ne with respect to the turbine rotational speed Nt increases in the horizontal axis direction of the command value map 13 shown in FIG.
- the linear solenoid valve SLT is instructed to raise L.
- the line pressure control means 11 follows the vertical axis direction of the command value map 13 shown in FIG. 4 so that the line pressure P increases as the rotational speed difference (Ne ⁇ Nt) from the turbine rotational speed Nt approaches the engine rotational speed Ne.
- the linear solenoid valve SLT is commanded to reduce the increase in L.
- the engine control unit (not shown) performs idle rotation to warm up the engine 2.
- the number is controlled to about 2100 [rpm], which is higher than 600 to 700 [rpm], which is a normal idle speed.
- the oil pump 21 also rotates at a higher speed than usual, so that the generated hydraulic pressure increases.
- the secondary regulator valve 25 also regulates the secondary pressure PSEC according to the hydraulic pressure of the linear solenoid valve SLT, that is, the linear solenoid valve so as to increase the line pressure PL.
- SLT pressure P SLT of the SLT is increased
- the secondary pressure P SEC that is the circulating hydraulic pressure of the torque converter 4 is also increased.
- the torque converter 4 than the normal secondary pressure Psec when control is performed in the normal line pressure P L (the first circulating oil pressure), elevated secondary pressure P SEC (second (Circulating oil pressure) increases the amount of oil supplied, and the oil in the torque converter 4 is quickly filled. Therefore, as shown in FIG. 5B, the turbine rotational speed Nt increases faster than the turbine rotational speed Nt- NON when the line pressure P L (secondary pressure P SEC ) is not increased. That is, the start of fluid transmission of the torque converter 4 is accelerated.
- elevated secondary pressure P SEC second (Circulating oil pressure
- the oil of the torque converter 4 can be quickly filled as described above, for example, even if the driver attempts to start the vehicle by switching the shift range from the parking range to the drive range immediately after the engine 2 is started, the torque converter 4 Since the transmission of the driving force returns immediately, the vehicle can be started with almost no sense of incongruity. At this time, since the lock-up clutch 7 is not engaged, the durability of the lock-up clutch 7 is not affected at all.
- the turbine rotation If the number Nt remains substantially constant, the line pressure P L is raised.
- the line pressure P L remain substantially constant for example the turbine speed Nt as described above is raised and then, when the turbine speed Nt approaches the engine speed Ne (the revolution speed difference is small), it means that there being oil reservoir in the torque converter 4, the line pressure P L is gradually moved downward, gradually to approach the normal control of the line pressure P L.
- the hydraulic pressure command value for increasing the line pressure P L (secondary pressure P SEC ) may be set to an appropriate value so that it does not occur.
- the hydraulic pressure command value is preferably set to a value as high as possible within a settable range in consideration of the volume of the torque converter 4, the leakage amount of the portion where oil leaks, the discharge capacity of the oil pump, and the like.
- the line pressure P L (secondary pressure P SEC ) increases when the engine 2 is started after the engine 2 has been stopped for a long period of time, it is supplied to various gears and bearings inside the automatic transmission mechanism 5. Even if the lubricated oil that has been dropped has fallen downward, the lubricating pressure (secondary pressure exhaust pressure) supplied to the lubricating oil passage 34 of the automatic transmission mechanism 5 also increases, and the amount of lubricating oil in the automatic transmission mechanism 5 is reduced. Therefore, the automatic transmission mechanism 5 can be protected and improved in durability.
- the automatic transmission (3) includes a fluid transmission device (4) that performs fluid transmission with oil filled with rotation of the drive source (2), A speed change mechanism (5) for shifting and outputting the output rotation of the fluid transmission device (4); A circulating hydraulic pressure regulating valve (25) for regulating the hydraulic pressure discharged from the oil pump (21) to a circulating hydraulic pressure ( PSEC ) circulating through the fluid transmission device (4), and the circulating hydraulic pressure regulating valve (25) A hydraulic control device (6) having a pressure regulating solenoid valve (SLT) for supplying a signal pressure; A drive source rotation acquisition unit (14) that acquires the rotation speed (Ne) of the drive source (2), and a fluid transmission device rotation acquisition unit (15) that acquires the output rotation speed (Nt) of the fluid transmission device (4).
- a drive source rotation acquisition unit (14) that acquires the rotation speed (Ne) of the drive source (2)
- a fluid transmission device rotation acquisition unit (15) that acquires the output rotation speed (Nt) of the fluid transmission device (4).
- a rotational speed difference (Ne ⁇ Nt) between an output rotational speed (Nt) of the fluid transmission device (4) and a rotational speed (Ne) of the drive source (2) is a predetermined rotational speed ( ⁇ N).
- the pressure regulating solenoid valve (SLT) is controlled so that the circulating hydraulic pressure (P SEC ) becomes the first circulating hydraulic pressure, and the output rotational speed (Nt) of the fluid transmission device (4)
- the rotational speed difference (Ne ⁇ Nt) with respect to the rotational speed (Ne) of the drive source (2) is greater than a predetermined rotational speed ( ⁇ N)
- the circulating hydraulic pressure (P SEC ) is greater than the first circulating hydraulic pressure.
- the pressure regulating solenoid valve so that the second circulating hydraulic pressure is also increased.
- the secondary pressure PSEC can be increased to quickly fill the torque converter 4 with oil, so without relying on a structure for preventing mechanical oil leakage, Without using the lock-up clutch 7, it is possible to prevent the occurrence of the lost driving force phenomenon when the engine 2 starts after a long-term stop.
- Patent Document 2 when the lockup engagement pressure is supplied to try to engage the lockup clutch, the torque is supplied by supplying the lockup engagement pressure. Oil will be filled in the converter, but if the lock-up clutch engages with the front cover etc. and comes into close contact with it, the escape path for the air accumulated in the torque converter will also be blocked. The oil filling speed of the torque converter due to the supply of becomes slow. Therefore, the filling speed is faster when the line pressure P L and the secondary pressure P SEC are increased and oil is filled in the torque converter 4 as in the present embodiment.
- control unit (1) is configured to transmit the fluid transmission device (Ne) to the rotational speed (Ne) of the drive source (2).
- the output rotational speed (Nt) of 4) approaches, the second circulating oil pressure is brought closer to the first circulating oil pressure.
- the automatic transmission (3) (see, for example, FIGS. 1 to 5) includes a fluid transmission device (4) that transmits fluid by oil filled with rotation of the drive source (2); A speed change mechanism (5) for shifting and outputting the output rotation of the fluid transmission device (4); A circulating hydraulic pressure regulating valve (25) for regulating the hydraulic pressure discharged from the oil pump (21) to a circulating hydraulic pressure ( PSEC ) circulating through the fluid transmission device (4), and the circulating hydraulic pressure regulating valve (25) A hydraulic control device (6) having a pressure regulating solenoid valve (SLT) for supplying a signal pressure; When the oil of the fluid transmission device (4) is filled, the pressure regulating solenoid valve (SLT) is controlled so that the circulating hydraulic pressure (P SEC ) becomes the first circulating hydraulic pressure, and the fluid transmission device When the oil in (4) is missing, the pressure regulating solenoid valve (SLT) is controlled so that the circulating oil pressure (P SEC ) becomes a second circulating oil pressure that is higher than the first circulating oil pressure
- the secondary pressure PSEC can be increased to quickly fill the torque converter 4 with oil. Therefore, the engine 2 can be used without relying on a structure for preventing mechanical oil loss. It is possible to prevent the occurrence of the lost phenomenon of the driving force when starting after a long-term stop.
- the control unit (1) acquires the rotational speed (Ne) of the drive source (2), and the fluid transmission device.
- the output rotation speed (Nt) of (4) is acquired, and based on the difference between the rotation speed (Ne) of the drive source (2) and the output rotation speed (Nt) of the fluid transmission device (4), the fluid transmission It is determined that the oil in the device (4) has been removed.
- oil leakage of the torque converter 4 can be accurately determined by simple control, compared to a case where oil leakage of the torque converter 4 is determined by measuring the time during which the engine 2 has been stopped.
- control unit (1) controls the drive source with respect to the output rotational speed (Nt) of the fluid transmission device (4).
- the rotational speed (Ne) of (2) is larger, the second circulating hydraulic pressure is increased more than the first circulating hydraulic pressure.
- control unit (1) is configured to control the fluid transmission device (Ne) with respect to the rotational speed (Ne) of the drive source (2). As the output rotational speed (Nt) of 4) approaches, the second circulating oil pressure is brought closer to the first circulating oil pressure.
- control unit (1) is configured such that the rotational speed (Ne) of the drive source (2) and the fluid transmission device (4).
- Ne rotational speed of the drive source (2)
- ⁇ N predetermined rotational speed
- control unit (1) is configured such that the rotational speed (Ne) of the drive source (2) and the fluid transmission device (4).
- the circulating hydraulic pressure (P SEC ) is increased by commanding a command value to the pressure regulating solenoid valve (SLT) based on the output rotational speed (Nt) of the fluid transmission device (4).
- the hydraulic control device (6) controls the oil pump (SLT) according to the signal pressure of the pressure regulating solenoid valve (SLT). 21) having a line pressure regulating valve (24) for regulating the hydraulic pressure discharged in step 21) to the line pressure (P L );
- the circulating hydraulic pressure regulating valve (25) regulates the exhaust pressure of the line pressure (P L ) to the circulating hydraulic pressure (P SEC ),
- the control unit (1) is an input torque calculated from a speed ratio (Ne / Nt) between the rotational speed (Ne) of the drive source (2) and the output rotational speed (Nt) of the fluid transmission device (4).
- the circulating hydraulic pressure (P SEC ) is controlled to be the first circulating hydraulic pressure, and the line pressure (P L ) is increased.
- the circulating hydraulic pressure (P SEC ) is controlled to be the second circulating hydraulic pressure by controlling the pressure regulating solenoid valve (SLT).
- control unit 1 without performing such complicated operations for increasing the secondary pressure P SEC, by simple control of only compute the command value of the line pressure P L to be applied to conventional linear solenoid valve SLT
- the secondary pressure PSEC can be increased.
- the first circulating hydraulic pressure is a hydraulic pressure that enables the power transmission of the fluid transmission device.
- the fluid transmission device (4) is engaged with a lock-up clutch (7 )
- the hydraulic control device (6) has a switching valve (26) for switching on and off the supply of the lockup engagement pressure
- the controller (1) controls the circulating hydraulic pressure (P SEC ) by controlling the pressure regulating solenoid valve (SLT) in a state where the switching valve (26) is turned off the supply of the lock-up engagement pressure. ) Is raised.
- the said control part (1) is the said circulation hydraulic pressure ( PSEC ) immediately after the said drive source (2) is started.
- the control to start the second circulating oil pressure is started.
- the oil shortage determining means 12 of the control unit 1 it is determined by the oil shortage determining means 12 of the control unit 1 whether or not the oil loss of the torque converter 4 has occurred. If the oil loss of the torque converter 4 is not determined, the line pressure P L running control based (the secondary pressure P SEC) to the normal throttle opening degree, the line pressure P L (the secondary pressure P SEC) rises above normal control when it is determined missing oil of the torque converter 4 However, when the turbine speed Nt does not increase in conjunction with the engine speed Ne although the automatic transmission mechanism 5 is in the neutral state, the oil in the torque converter 4 is drained.
- the control unit 1 determines the oil loss in the torque converter 4 by (oil shortage determination unit 12) is not particularly performed, based on the line pressure P L of the normal control To, may have been configured to control so as to increase the rotational speed difference between the engine speed Ne and the turbine speed Nt to (Ne-Nt) The larger the line pressure P L (the secondary pressure P SEC).
- the rotational speed difference between the engine speed Ne and turbine speed Nt (Ne-Nt) becomes the normal line pressure P L as long as the rotational speed difference when the oil in the torque converter 4 is filled since command value map 13 is set as the oil of the torque converter 4 is to settle the line pressure P L naturally normal control when it is filled.
- the oil shortage determining means 12 of the control unit 1 determines oil loss of the torque converter 4 on the basis of the rotational speed difference (Ne ⁇ Nt) between the engine rotational speed Ne and the turbine rotational speed Nt.
- the present invention is not limited to this, and any method may be used as long as oil loss of the torque converter 4 can be determined.
- the oil loss of the torque converter 4 is proportional to the time (period) during which the engine 2 is stopped, and the way of the oil loss is calculated or experimentally determined from the structure of the torque converter 4. It is also possible to provide time-counting means for determining the oil loss of the torque converter 4 based on the timed stop period.
- the time measuring means for measuring the stop period of the engine 2 may be provided in the control unit 1 of the automatic transmission, or provided in another control unit (for example, the engine control unit) or car navigation to notify the stop period therefrom. You may make it acquire by receiving a signal.
- the oil shortage determining means 12 of the control unit 1 determines oil loss of the torque converter 4 on the basis of the rotational speed difference (Ne ⁇ Nt) between the engine rotational speed Ne and the turbine rotational speed Nt.
- the oil drainage of the torque converter 4 may be determined, that is, the engine rotational speed Ne.
- any method may be used.
- the vehicle in which the automatic transmission is mounted with only the engine 2 has been described.
- the engine and the motor generator are used as drive sources, and the driving force of the drive source is transmitted by the torque converter.
- It may be a hybrid vehicle.
- the line pressure is increased based on the hydraulic pressure generated by an electric oil pump or the like even when the engine does not start immediately when the vehicle start switch is pressed and the EV travel mode is set.
- the oil filling of the torque converter can be accelerated.
- the command value map 13 may be corrected so that the command value is further increased particularly when the oil temperature is low and the oil viscosity is high.
- the command value map may be obtained at any time without the command value map. In this case as well, the command value may be calculated in consideration of the oil temperature or the like.
- the fluid transmission device is a torque converter.
- any fluid transmission device may be used as long as it can transmit a driving force such as fluid coupling. Absent.
- the automatic transmission can be used for an automatic transmission mounted on a vehicle such as a passenger car or a truck. In particular, it is required to prevent the occurrence of a lost driving force at the time of start after a long-term engine stop. It is suitable for use in things.
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Abstract
Description
駆動源の回転を充填された油により流体伝動する流体伝動装置と、
前記流体伝動装置の出力回転を変速して出力する変速機構と、
オイルポンプで吐出された油圧を前記流体伝動装置を循環する循環油圧に調圧する循環油圧調圧バルブと、前記循環油圧調圧バルブに信号圧を供給する調圧ソレノイドバルブと、を有する油圧制御装置と、
前記駆動源の回転速度を取得する駆動源回転取得部と、前記流体伝動装置の出力回転速度を取得する流体伝動装置回転取得部と、を有し、前記流体伝動装置の出力回転速度と前記駆動源の回転速度との回転速度差が所定回転速度以下の場合には前記循環油圧が第1の循環油圧となるように前記調圧ソレノイドバルブを制御し、前記流体伝動装置の出力回転速度と前記駆動源の回転速度との回転速度差が所定回転速度よりも大きい場合には前記循環油圧が前記第1の循環油圧よりも上昇した第2の循環油圧となるように前記調圧ソレノイドバルブを制御する制御部と、を備える。
前記流体伝動装置(4)の出力回転を変速して出力する変速機構(5)と、
オイルポンプ(21)で吐出された油圧を前記流体伝動装置(4)を循環する循環油圧(PSEC)に調圧する循環油圧調圧バルブ(25)と、前記循環油圧調圧バルブ(25)に信号圧を供給する調圧ソレノイドバルブ(SLT)と、を有する油圧制御装置(6)と、
前記駆動源(2)の回転速度(Ne)を取得する駆動源回転取得部(14)と、前記流体伝動装置(4)の出力回転速度(Nt)を取得する流体伝動装置回転取得部(15)と、を有し、前記流体伝動装置(4)の出力回転速度(Nt)と前記駆動源(2)の回転速度(Ne)との回転速度差(Ne-Nt)が所定回転速度(ΔN)以下の場合には前記循環油圧(PSEC)が第1の循環油圧となるように前記調圧ソレノイドバルブ(SLT)を制御し、前記流体伝動装置(4)の出力回転速度(Nt)と前記駆動源(2)の回転速度(Ne)との回転速度差(Ne-Nt)が所定回転速度(ΔN)よりも大きい場合には前記循環油圧(PSEC)が前記第1の循環油圧よりも上昇した第2の循環油圧となるように前記調圧ソレノイドバルブ(SLT)を制御する制御部(1)と、を備える。
前記流体伝動装置(4)の出力回転を変速して出力する変速機構(5)と、
オイルポンプ(21)で吐出された油圧を前記流体伝動装置(4)を循環する循環油圧(PSEC)に調圧する循環油圧調圧バルブ(25)と、前記循環油圧調圧バルブ(25)に信号圧を供給する調圧ソレノイドバルブ(SLT)と、を有する油圧制御装置(6)と、
前記流体伝動装置(4)の油が充填されている場合には前記循環油圧(PSEC)が第1の循環油圧となるように前記調圧ソレノイドバルブ(SLT)を制御し、前記流体伝動装置(4)の油が抜けている場合には前記循環油圧(PSEC)が前記第1の循環油圧よりも上昇した第2の循環油圧となるように前記調圧ソレノイドバルブ(SLT)を制御する制御部(1)と、を備える。
前記循環油圧調圧バルブ(25)は、前記ライン圧(PL)の排圧を前記循環油圧(PSEC)に調圧し、
前記制御部(1)は、前記駆動源(2)の回転速度(Ne)と前記流体伝動装置(4)の出力回転速度(Nt)との速度比(Ne/Nt)から算出される入力トルクに応じて前記調圧ソレノイドバルブ(SLT)を制御することで前記循環油圧(PSEC)が前記第1の循環油圧となるように制御し、前記ライン圧(PL)を上昇するように前記調圧ソレノイドバルブ(SLT)を制御することで前記循環油圧(PSEC)が前記第2の循環油圧となるように制御する。
前記油圧制御装置(6)は、前記ロックアップ係合圧の供給をオン・オフ切換えする切換えバルブ(26)を有し、
前記制御部(1)は、前記切換えバルブ(26)が前記ロックアップ係合圧の供給をオフしている状態で、前記調圧ソレノイドバルブ(SLT)を制御することにより前記循環油圧(PSEC)を上昇させることを特徴とする。
2…駆動源(エンジン)
3…自動変速機
4…流体伝動装置(トルクコンバータ)
5…変速機構(自動変速機構)
6…油圧制御装置
7…ロックアップクラッチ
13…指令値マップ
14…駆動源回転取得部(エンジン回転速度取得手段)
15…流体伝動装置回転取得部(タービン回転速度取得手段)
21…オイルポンプ
24…ライン圧調圧バルブ(プライマリレギュレータバルブ)
25…循環油圧調圧バルブ(セカンダリレギュレータバルブ)
26…切換えバルブ(ロックアップリレーバルブ)
Ne…駆動源の回転速度(エンジン回転数)
Nt…流体伝動装置の出力回転速度(タービン回転数)
PSEC…循環油圧(セカンダリ圧)
PL…ライン圧
SLT…調圧ソレノイドバルブ(リニアソレノイドバルブ)
Claims (12)
- 駆動源の回転を充填された油により流体伝動する流体伝動装置と、
前記流体伝動装置の出力回転を変速して出力する変速機構と、
オイルポンプで吐出された油圧を前記流体伝動装置を循環する循環油圧に調圧する循環油圧調圧バルブと、前記循環油圧調圧バルブに信号圧を供給する調圧ソレノイドバルブと、を有する油圧制御装置と、
前記駆動源の回転速度を取得する駆動源回転取得部と、前記流体伝動装置の出力回転速度を取得する流体伝動装置回転取得部と、を有し、前記流体伝動装置の出力回転速度と前記駆動源の回転速度との回転速度差が所定回転速度以下の場合には前記循環油圧が第1の循環油圧となるように前記調圧ソレノイドバルブを制御し、前記流体伝動装置の出力回転速度と前記駆動源の回転速度との回転速度差が所定回転速度よりも大きい場合には前記循環油圧が前記第1の循環油圧よりも上昇した第2の循環油圧となるように前記調圧ソレノイドバルブを制御する制御部と、を備える、
自動変速機。 - 前記制御部は、前記駆動源の回転速度に対して前記流体伝動装置の出力回転速度が近づくほど前記第2の循環油圧を前記第1の循環油圧に近づける、
請求項1に記載の自動変速機。 - 駆動源の回転を充填された油により流体伝動する流体伝動装置と、
前記流体伝動装置の出力回転を変速して出力する変速機構と、
オイルポンプで吐出された油圧を前記流体伝動装置を循環する循環油圧に調圧する循環油圧調圧バルブと、前記循環油圧調圧バルブに信号圧を供給する調圧ソレノイドバルブと、を有する油圧制御装置と、
前記流体伝動装置の油が充填されている場合には前記循環油圧が第1の循環油圧となるように前記調圧ソレノイドバルブを制御し、前記流体伝動装置の油が抜けている場合には前記循環油圧が前記第1の循環油圧よりも上昇した第2の循環油圧となるように前記調圧ソレノイドバルブを制御する制御部と、を備える、
自動変速機。 - 前記制御部は、前記駆動源の回転速度を取得し、前記流体伝動装置の出力回転速度を取得し、前記駆動源の回転速度と前記流体伝動装置の出力回転速度との違いに基づき、前記流体伝動装置の油が抜けていることを判定する、
請求項3に記載の自動変速機。 - 前記制御部は、前記流体伝動装置の出力回転速度に対して前記駆動源の回転速度が大きいほど前記第2の循環油圧を前記第1の循環油圧よりも大きく上昇させる、
請求項4に記載の自動変速機。 - 前記制御部は、前記駆動源の回転速度に対して前記流体伝動装置の出力回転速度が近づくほど前記第2の循環油圧を前記第1の循環油圧に近づける、
請求項5に記載の自動変速機。 - 前記制御部は、前記駆動源の回転速度と前記流体伝動装置の出力回転速度との差が所定回転速度よりも大きい場合に、前記流体伝動装置の油が抜けていることを判定する、
請求項4ないし6のいずれか1項に記載の自動変速機。 - 前記制御部は、前記駆動源の回転速度と前記流体伝動装置の出力回転速度と前記調圧ソレノイドバルブに指令する指令値との対応関係を記録した指令値マップに従って、前記駆動源の回転速度と前記流体伝動装置の出力回転速度とに基づき前記調圧ソレノイドバルブに指令値を指令することで前記循環油圧を上昇させる、
請求項1ないし7のいずれか1項に記載の自動変速機。 - 前記油圧制御装置は、前記調圧ソレノイドバルブの信号圧に応じて、前記オイルポンプで吐出された油圧をライン圧に調圧するライン圧調圧バルブを有し、
前記循環油圧調圧バルブは、前記ライン圧の排圧を前記循環油圧に調圧し、
前記制御部は、前記駆動源の回転速度と前記流体伝動装置の出力回転速度との速度比から算出される入力トルクに応じて前記調圧ソレノイドバルブを制御することで前記循環油圧が前記第1の循環油圧となるように制御し、前記ライン圧を上昇するように前記調圧ソレノイドバルブを制御することで前記循環油圧が前記第2の循環油圧となるように制御する、
請求項1ないし8のいずれか1項に記載の自動変速機。 - 前記第1の循環油圧は、前記流体伝動装置の動力伝達が可能となる油圧である、
請求項1ないし9のいずれか1項に記載の自動変速機。 - 前記流体伝動装置は、ロックアップ係合圧が供給されることで係合するロックアップクラッチを有し、
前記油圧制御装置は、前記ロックアップ係合圧の供給をオン・オフ切換えする切換えバルブを有し、
前記制御部は、前記切換えバルブが前記ロックアップ係合圧の供給をオフしている状態で、前記調圧ソレノイドバルブを制御することにより前記循環油圧を上昇させる、
請求項1ないし10のいずれか1項に記載の自動変速機。 - 前記制御部は、前記駆動源が始動された直後に、前記循環油圧を前記第2の循環油圧にする制御を開始する、
ことを特徴とする請求項1ないし11のいずれか1項に記載の自動変速機。
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CN110242743B (zh) * | 2018-03-09 | 2021-01-22 | 上海汽车集团股份有限公司 | 一种液力变矩器的控制方法及控制系统 |
CN110985662A (zh) * | 2020-02-28 | 2020-04-10 | 盛瑞传动股份有限公司 | 一种防止自动变速器离合器故障的控制方法 |
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