WO2015098950A1 - 自動変速機の油圧制御装置 - Google Patents
自動変速機の油圧制御装置 Download PDFInfo
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- WO2015098950A1 WO2015098950A1 PCT/JP2014/084123 JP2014084123W WO2015098950A1 WO 2015098950 A1 WO2015098950 A1 WO 2015098950A1 JP 2014084123 W JP2014084123 W JP 2014084123W WO 2015098950 A1 WO2015098950 A1 WO 2015098950A1
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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
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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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
- F16H61/0202—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 electric
- F16H61/0204—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 electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0206—Layout of electro-hydraulic control circuits, e.g. arrangement of valves
- F16H2061/0209—Layout of electro-hydraulic control circuits, e.g. arrangement of valves with independent solenoid valves modulating the pressure individually for each clutch or brake
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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
- 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
- F16H2061/1256—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected
- F16H2061/126—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected the failing part is the controller
- F16H2061/1264—Hydraulic parts of the controller, e.g. a sticking valve or clogged channel
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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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
- F16H61/68—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 specially adapted for stepped gearings
- F16H61/684—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 specially adapted for stepped gearings without interruption of drive
- F16H61/686—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 specially adapted for stepped gearings without interruption of drive with orbital gears
Definitions
- the present invention relates to a hydraulic control device for an automatic transmission having a plurality of engagement elements mounted on a vehicle, for example, and more specifically to an off-fail of a linear solenoid valve capable of supplying hydraulic pressure to a hydraulic servo of a plurality of engagement elements.
- the present invention relates to a hydraulic control device for an automatic transmission having a limp home function.
- a stepped automatic transmission mounted on a vehicle controls the engagement state of a plurality of engagement elements (clutch, brake) by a hydraulic control device, and forms a transmission path in a transmission mechanism at each shift stage.
- a hydraulic control device includes a linear solenoid valve that can supply hydraulic pressure to a hydraulic servo for engaging and disengaging each engagement element, and all the solenoid valves such as the plurality of linear solenoid valves are off-failed.
- a limp home function for an all-off failure that is, a function for forming a gear stage so that the vehicle can be driven even during an all-off failure) has become widespread.
- This hydraulic control device is equipped with a fail-safe valve that outputs a range pressure as the limp home pressure during all-off failure of the solenoid valve. Further, in this hydraulic control device, when the solenoid valve is not generating an all-off failure, oil discharged from the drain port of the linear solenoid valve is discharged through the drain check valve after passing through the fail-safe valve.
- the hydraulic control device (50) of the automatic transmission (1) is an automatic transmission capable of forming a plurality of shift stages by selectively engaging a plurality of engagement elements (C1).
- a normally closed first solenoid valve (SL1) capable of supplying hydraulic pressure to the hydraulic servo (60) of the engagement element (C1);
- the first input port (61a) communicating with the drain port (66) of the first solenoid valve (SL1), the first drain port (61b), the first input port (61a), and the first
- the first movable member (61p) capable of switching between communication and blocking of one drain port (61b), and the first input port (61a) and the first drain port (61b) are blocked.
- a first check valve (61) having first biasing means (61s) biasing the first movable member (61p);
- a fail-safe valve having a fail pressure output port (51d, 51g, 51j) for switching to a fail position and outputting a predetermined oil pressure (PD, PR) when the first solenoid valve (SL1) fails in a non-energized state.
- the first movable member (61p) of the first check valve (61) includes the first input port (61a) and the first movable port (61a) and the first solenoid valve (SL1) during the failure when the first solenoid valve (SL1) is deenergized.
- the first drain port (61b) is biased to be shut off.
- the fail-safe valve is switched to the fail position, and the first movable member of the first check valve shuts off the first input port and the first drain port. Energized and locked off.
- the predetermined oil pressure output from the fail pressure output port acts to communicate the second input port and the output port with the second check valve.
- the second urging means urges the second input port and the output port to shut off, but allows the second input port and the output port to communicate with each other at a hydraulic pressure lower than a predetermined hydraulic pressure.
- the hydraulic pressure that has passed through the second check valve reaches the side that opens the first input port of the first check valve.
- the hydraulic pressure is supplied and increased.
- the hydraulic pressure is reduced in order to open the second check valve, when the hydraulic pressure that has passed through the second check valve reaches the first input port, the lock pressure and the first biasing means. It is smaller than the locking force. Accordingly, the hydraulic pressure output from the second check valve is reversely input to the drain port of the first solenoid valve without opening the first check valve, and the hydraulic pressure is supplied to the hydraulic servo to enable control. be able to.
- the first solenoid valve and the first check valve are in direct communication with each other.
- the oil passage that communicates the first solenoid valve and the first check valve can be shortened, and a decrease in controllability due to an increase in flow resistance and an increase in size of the hydraulic control device can be suppressed.
- the first movable member is attached so as to shut off the first input port and the first drain port during a failure in which the first solenoid valve is de-energized.
- the means for urging the first movable member is not particularly limited.
- a hydraulic pressure such as a range pressure is supplied as the lock pressure, or a mechanical external force such as a member or mechanism other than the hydraulic pressure is supplied. May be energized. Thereby, the freedom degree of design can be improved.
- FIG. 3 is a schematic diagram illustrating a hydraulic pressure supply state when a forward gear is selected in a normal state in the hydraulic control device according to the embodiment of the present invention.
- FIG. 3 is a schematic diagram illustrating a hydraulic pressure supply state when a reverse gear is selected in a normal state in the hydraulic control device according to the embodiment of the present invention.
- FIG. 3 is a schematic diagram showing a hydraulic pressure supply state when a forward gear is selected during limp home in the hydraulic control device according to the embodiment of the present invention.
- the schematic which shows the hydraulic pressure supply state when the reverse stage is selected at the time of limp home. It is an enlarged view of each part of the hydraulic control apparatus which concerns on embodiment of this invention, (a) is a linear solenoid valve, a drain check valve, and a delay check valve, (b) is a fail safe valve.
- the automatic transmission 1 is connected to a crankshaft of an engine (internal combustion engine) (not shown) or a rotor of an electric motor as a drive source mounted vertically in a front portion of a rear wheel drive vehicle. Power (torque) from an engine or the like can be transmitted to left and right rear wheels (drive wheels) (not shown).
- the automatic transmission 1 shifts the power transmitted to the input shaft (input member) 40 from the starting device (fluid transmission device) 2, the oil pump 3, the engine, etc., and transmits it to the output shaft (output member) 41.
- a transmission mechanism 4 and a transmission case 5 that accommodates these are provided.
- the starting device 2 includes a lock-up clutch 21 capable of connecting and disconnecting the torque converter 20, a front cover coupled to an engine crankshaft and the like and the input shaft 40 of the transmission mechanism 4, and an input of the front cover and the transmission mechanism 4.
- a damper mechanism 22 that attenuates vibration between the shaft 40 and the shaft 40 is provided.
- the torque converter 20 is arranged inside the pump impeller 23 on the input side connected to the front cover, the turbine runner 24 on the output side connected to the input shaft 40 of the transmission mechanism 4, and the pump impeller 23 and the turbine runner 24.
- a stator 25 that rectifies the flow of hydraulic oil from the turbine runner 24 to the pump impeller 23, and a one-way clutch 26 that is supported by a stator shaft (not shown) and restricts the rotational direction of the stator 25 in one direction.
- the torque converter 20 may be a fluid coupling that does not have the stator 25.
- the oil pump 3 includes a pump assembly including a pump body and a pump cover, an external gear (inner rotor) connected to the pump impeller 23 of the torque converter 20 via a chain or a gear train, and an internal gear meshing with the external gear. It is comprised as a gear pump which has a tooth gear (outer rotor) etc.
- the oil pump 3 is driven by power from an engine or the like, sucks hydraulic oil stored in an oil pan (not shown), and pumps it to a hydraulic control device 50 described later.
- the transmission mechanism 4 is configured as a 10-speed transmission, and includes an input shaft 40, an output shaft 41 connected to left and right rear wheels via a differential gear and a drive shaft (not shown), an input shaft 40, and A Ravigneaux type planetary gear mechanism configured by combining a single pinion type first planetary gear 42 and a second planetary gear 43 arranged side by side in the axial direction of the output shaft 41, a double pinion type planetary gear, and a single pinion type planetary gear. And a planetary gear set 44. Further, the speed change mechanism 4 includes a first clutch C1, a second clutch C2, a third clutch C3, a first clutch C6 as six engagement elements for changing the power transmission path from the input shaft 40 to the output shaft 41. 4 clutch C4, 1st brake B1, and 2nd brake B2 are provided.
- the first and second planetary gears 42 and 43 and the planetary gear set 44 are referred to as the planetary gear set 44, the second planetary gear 43, and the first planetary gear 42 from the starting device 2, that is, the engine side (left side in FIG. 1). It arrange
- the planetary gear set 44 is disposed on the front side of the vehicle so as to be close to the starting device 2
- the first planetary gear 42 is disposed on the rear side of the vehicle so as to be close to the output shaft 41
- 43 is disposed between the planetary gear set 44 and the first planetary gear 42.
- the first planetary gear 42 is connected to a first sun gear 42s that is an external gear, a first ring gear 42r that is an internal gear arranged concentrically with the first sun gear 42s, and a first sun gear 42s and a first ring gear 42r, respectively.
- the first carrier 42c of the first planetary gear 42 is always connected (fixed) to the intermediate shaft 47 of the transmission mechanism 4 connected to the input shaft 40.
- the first carrier 42c functions as an input element of the first planetary gear 42 when the fourth clutch C4 is engaged, and idles when the fourth clutch C4 is released.
- the first ring gear 42r functions as an output element of the first planetary gear 42 when the fourth clutch C4 is engaged.
- the second planetary gear 43 includes a second sun gear 43s that is an external gear, a second ring gear 43r that is an internal gear arranged concentrically with the second sun gear 43s, and the second sun gear 43s and the second ring gear 43r, respectively.
- the second sun gear 43 s of the second planetary gear 43 is integrated (always connected) with the first sun gear 42 s of the first planetary gear 42, so that the second sun gear 43 s rotates or stops constantly (and coaxially) with the first sun gear 42 s. It has become.
- the first sun gear 42 s and the second sun gear 43 s may be configured separately and always connected via a connecting member (not shown).
- the second carrier 43c of the second planetary gear 43 is always connected to the output shaft 41, and is always rotated or stopped integrally (and coaxially) with the output shaft 41.
- the second carrier 43 c functions as an output element of the second planetary gear 43.
- the second ring gear 43 r of the second planetary gear 43 functions as an element that can be fixed to the second planetary gear 43.
- the planetary gear set 44 is a compound planetary gear mechanism configured by combining a third planetary gear 45 that is a double pinion planetary gear and a fourth planetary gear 46 that is a single pinion planetary gear.
- Each planetary gear is arranged in the transmission case 5 so as to be arranged in the order of the fourth planetary gear 46, the third planetary gear 45, the second planetary gear 43, and the first planetary gear 42 from the engine side.
- the planetary gear set 44 includes a third sun gear 45s and a fourth sun gear 46s that are external gears, a third ring gear 45r that is an internal gear disposed concentrically with the third and fourth sun gears 45s and 46s, and a third gear.
- the third carrier 45c holds the plurality of third pinion gears 45p and the plurality of fourth pinion gears 46p so as to be rotatable (rotatable) and revolved.
- the third planetary gear 45 includes a third sun gear 45s, a third carrier 45c, a third pinion gear 45p, a fourth pinion gear 46p, and a third ring gear 45r.
- the fourth planetary gear 46 includes a fourth sun gear 46s, a third carrier 45c, a fourth pinion gear 46p, and a third ring gear 45r.
- the fourth sun gear 46s functions as an element that can be fixed to the planetary gear set 44.
- the third carrier 45 c is always connected (fixed) to the input shaft 40 and is always connected to the first carrier 42 c of the first planetary gear 42 via the intermediate shaft 47.
- the third carrier 45 c functions as an input element of the planetary gear set 44.
- the third ring gear 45 r functions as a first output element of the planetary gear set 44
- the third sun gear 45 s functions as a second output element of the planetary gear set 44.
- the first clutch C1 connects the first sun gear 42s of the first planetary gear 42 and the second sun gear 43s of the second planetary gear 43 that are always connected to the third ring gear 45r of the planetary gear set 44, and releases the connection between them.
- the second clutch C2 connects the first sun gear 42s of the first planetary gear 42 and the second sun gear 43s of the second planetary gear 43 and the third sun gear 45s of the planetary gear set 44 that are always connected to each other and releases the connection therebetween.
- the third clutch C3 connects the second ring gear 43r of the second planetary gear 43 and the third ring gear 45r of the planetary gear set 44 to each other and releases the connection between them.
- the fourth clutch C4 connects the first ring gear 42r of the first planetary gear 42 and the output shaft 41 to each other and releases the connection therebetween.
- the first brake B1 fixes (connects) the fourth sun gear 46s of the planetary gear set 44 to the transmission case 5 in a non-rotatable manner and releases the fourth sun gear 46s to the transmission case 5 so as to be rotatable.
- the second brake B2 fixes (connects) the second ring gear 43r of the second planetary gear 43 to the transmission case 5 in a non-rotatable manner and releases the second ring gear 43r to the transmission case 5 so as to be rotatable. It is.
- first clutch C1 to the fourth clutch C4 a piston, a plurality of friction engagement plates (for example, a friction plate formed by sticking a friction material on both surfaces of an annular member, and both surfaces are smoothed)
- a multi-plate friction type hydraulic clutch having a hydraulic servo constituted by an engagement oil chamber, a centrifugal hydraulic pressure cancellation chamber, and the like, each of which is supplied with hydraulic oil, is employed.
- the first brake B1 and the second brake B2 include a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, and the like.
- a plate friction type hydraulic brake is adopted.
- the automatic transmission 1 engages a hydraulic servo 60 capable of engaging / disengaging the first clutch C1, a hydraulic servo 70 capable of engaging / disengaging the second clutch C2, a hydraulic servo 80 capable of engaging / disengaging the third clutch C3, and a fourth clutch C4.
- a hydraulic servo (not shown) that can be disengaged, a hydraulic servo (not shown) that can disengage the first brake B1, and a hydraulic servo 90 that can disengage the second brake B2 are provided (see FIG. 4).
- the hydraulic servos of the first to fourth clutches C1 to C4, the first brake B1, and the second brake B2 are operated by receiving and supplying hydraulic oil from the hydraulic control device 50.
- FIG. 2 (a) is an engagement table showing the relationship between each gear position of the transmission mechanism 4 and the operating states of the first clutch C1 to the fourth clutch C4, the first brake B1, and the second brake B2.
- FIG. 3 is a velocity diagram showing the ratio of the rotational speed of each rotary element to the rotational speed of the input shaft 40 in the speed change mechanism 4 (however, the input shaft 40, that is, the first carrier 42c and the third carrier 45c). The rotation speed is set to 1).
- the three rotating elements constituting the single-pinion type first planetary gear 42 are velocity diagrams of the first planetary gear 42 (
- the first sun gear 42s, the first carrier 42c, and the first ring gear 42r are arranged in this order from the left side in the drawing at intervals corresponding to the gear ratio ⁇ 1.
- the first sun gear 42s is the first rotating element of the automatic transmission 1
- the first carrier 42c is the second rotating element of the automatic transmission 1
- the first ring gear 42r is the third rotating element of the automatic transmission 1. Therefore, the first planetary gear 42 includes the first rotation element, the second rotation element, and the third rotation element of the automatic transmission 1 that are arranged in order at intervals corresponding to the gear ratio ⁇ 1 on the velocity diagram.
- the three rotating elements constituting the single-pinion type second planetary gear 43 are speed diagrams of the second planetary gear 43 (the center in FIG. 3).
- the second sun gear 43s, the second carrier 43c, and the second ring gear 43r are arranged in this order from the left side in the drawing at intervals corresponding to the gear ratio ⁇ 2.
- the second sun gear 43s is the fourth rotating element of the automatic transmission 1
- the second carrier 43c is the fifth rotating element of the automatic transmission 1
- the second ring gear 43r is the sixth rotating element of the automatic transmission 1. Therefore, the second planetary gear 43 has the fourth rotation element, the fifth rotation element, and the sixth rotation element of the automatic transmission 1 that are arranged in order at intervals corresponding to the gear ratio ⁇ 2 on the speed diagram.
- the four rotating elements constituting the planetary gear set 44 that is, the fourth sun gear 46s, the third carrier 45c, the third ring gear 45r, and the third sun gear 45s are arranged in this order from the left side of the drawing in the single type third planetary gear 45. They are arranged on a speed diagram (speed diagram on the right side in FIG. 3) of the planetary gear set 44 with an interval corresponding to the gear ratio ⁇ 3 and the gear ratio ⁇ 4 of the double pinion type fourth planetary gear 46.
- the fourth sun gear 46s is the seventh rotating element of the automatic transmission 1
- the third carrier 45c is the eighth rotating element of the automatic transmission 1
- the third ring gear 45r is the ninth rotating element of the automatic transmission 1
- the third sun gear 45s is the tenth rotating element of the automatic transmission 1.
- the planetary gear set 44 has the seventh rotation element, the eighth rotation element, the ninth rotation element, and the tenth rotation of the automatic transmission 1 that are arranged in order on the speed diagram at intervals corresponding to the gear ratios ⁇ 3 and ⁇ 4. Has elements.
- each of the first to fourth clutches C1 to C4, the first brake B1, and the second brake B2 shown in the skeleton diagram of FIG. By engaging and disengaging in the combinations shown in the table, the first forward speed (1st) to the tenth forward speed (10th) and the first reverse speed (Rev) at the rotation speed ratio as shown in the speed diagram of FIG. Is achieved.
- the hydraulic control device 50 of the automatic transmission 1 will be described.
- the actual spool is one in each valve.
- the hydraulic control device 50 includes an oil pump (not shown) and a primary regulator valve that regulates the hydraulic pressure from the oil pump to the line pressure PL, and generates various source pressures by regulating them.
- the hydraulic pressure control device 50 includes a manual valve 52 that generates the forward range pressure PD and the reverse range pressure PR from the line pressure PL by being switched by a shift lever.
- the manual valve 52 includes an input port 52a to which the line pressure PL is input, a forward range pressure output port 52b that outputs the line pressure PL as the forward range pressure PD when the shift lever is in the forward range, and a shift lever in the reverse range.
- the hydraulic control device 50 includes a linear solenoid valve (first solenoid valve) SL1, a linear solenoid valve (solenoid valve) SL2, and a linear solenoid valve (solenoid valve) SL3 that can supply hydraulic pressure to the hydraulic servo of each engagement element.
- a linear solenoid valve (solenoid valve) (not shown) for controlling the fourth clutch C4 a linear solenoid valve (solenoid valve) (not shown) for controlling the first brake, a linear solenoid valve (solenoid valve) SL6, a solenoid A valve (second solenoid valve) SR is provided.
- linear solenoid valves SL1 to SL6 are normally closed (N) which is disconnected from the input port and the output port when not energized (hereinafter also referred to as OFF) and communicates when energized (hereinafter also referred to as ON). / C) type is used.
- the solenoid valve SR is of a normally open (N / O) type.
- the linear solenoid valve SL1 includes an input port 64, an output port 65, and a drain port 66, and is electrically controlled by an ECU (not shown).
- a forward range pressure PD can be input to the input port 64.
- the output port 65 is in communication with the hydraulic servo 60 of the first clutch C1.
- the drain port 66 communicates with the drain check valve 61.
- the linear solenoid valve SL1 is closed when no control signal is input from the ECU, and the forward range pressure PD input to the input port 64 is shut off. At this time, the drain port 66 and the output port 65 communicate with each other.
- the linear solenoid valve SL1 is opened when a control signal is input from the ECU, and the forward range pressure PD input to the input port 64 is output from the output port 65 and supplied to the hydraulic servo 60. It is like that.
- the linear solenoid valve SL2 includes an input port 74 through which the line pressure PL can be input, an output port 75 communicated with the hydraulic servo 70 of the second clutch C2, and a drain port 76 communicated with the drain check valve 71. Yes.
- the linear solenoid valve SL3 includes an input port 84 through which the forward range pressure PD or the reverse range pressure PR can be input, an output port 85 communicated with the hydraulic servo 80 of the third clutch C3, and a drain communicated with the drain check valve 81. Port 86.
- the linear solenoid valve SL6 includes an input port 94 through which the line pressure PL can be input, an output port 95 communicated with the hydraulic servo 90 of the second brake B2, and a drain port 96 communicated with the drain check valve 91. Yes.
- the hydraulic control device 50 includes a fail-safe valve 51 capable of realizing a limp home function using the forward range pressure PD or the reverse range pressure PR, and a three-way valve (selection mechanism) 53.
- the gear position at the limp home is configured to be the seventh forward speed in the forward range, and the reverse speed is formed in the reverse range, and is operated by operating the shift lever.
- the manual valve 52 is switched, it is assumed that the vehicle can travel by switching between the seventh forward speed and the reverse speed.
- the first clutch C1, the second clutch C2, and the third clutch C3 are simultaneously engaged to form the seventh forward speed, or the second clutch C2, the third clutch C3, and the second brake B2 Can be engaged at the same time to form a reverse gear or can be switched. That is, in the seventh forward speed and the reverse speed, the two engagement elements of the second clutch C2 and the third clutch C3 are common.
- the three-way valve (so-called shuttle valve) 53 includes a first input port 53a through which the forward range pressure PD can be input, a second input port 53b through which the reverse range pressure PR can be input, and an output port 53c.
- the output of the forward range pressure PD and the reverse range pressure PR is output from the output port 53c. It becomes like this.
- the fail-safe valve 51 includes a spool 51p and a spring 51s that urges the spool 51p upward in the drawing, and a first oil above the spool 51p.
- the forward range pressure input port 51e can receive the forward range pressure PD, and the forward output port 51d communicates with the drain port 66 of the linear solenoid valve SL1.
- the original pressure input port 51h can receive the forward range pressure PD or the reverse range pressure PR, and communicates with the output port 53c of the three-way valve 53.
- the common output port 51g is the drain port 76 of the linear solenoid valve SL2.
- the reverse range pressure input port 51k can receive the reverse range pressure PR, and the reverse output port 51j communicates with the drain port 96 of the linear solenoid valve SL6.
- the common output port 51g is a solenoid capable of supplying hydraulic pressure to the hydraulic servos 70 and 80 of the second clutch C2 and the third clutch C3, which are some of the engagement elements common to the seventh forward speed and the reverse speed.
- the valves SL2 and SL3 are connected to drain ports 76 and 86.
- the forward output port 51d is a second engagement element that is a part of the first clutch C1, the second clutch C2, and the third clutch C3, which are the three engagement elements that form the seventh forward speed.
- the solenoid valve SL1 communicates with a drain port 66 capable of supplying hydraulic pressure to the hydraulic servo 60 of the first clutch C1, which is an engaging element other than the clutch C2 and the third clutch C3.
- the reverse output port 51j is a second clutch C2 that is a part of the engagement elements of the second clutch C2, the third clutch C3, and the second brake B2 that form the reverse gear. And it is connected to the drain port 96 of the solenoid valve SL6 that can supply hydraulic pressure to the hydraulic servo 90 of the second brake B2, which is an engaging element other than the third clutch C3.
- a biasing force of a spring 51s acts on the spool 51p in opposition to the signal pressure from the solenoid valve SR, so that the spool 51p has a normal position (left half position) on the upper side in the figure and a fail position (right side on the lower side in the figure). Half position).
- the forward output port 51d and the first drain port 51c are released in communication
- the common output port 51g and the second drain port 51f are released in communication
- the reverse output port 51j is released.
- the third drain port 51i is communicated and released.
- the forward range pressure input port 51e when the spool 51p is in the normal position, the forward range pressure input port 51e, the original pressure input port 51h, and the reverse range pressure input port 51k are blocked.
- the forward output port 51d and the forward range pressure input port 51e communicate with each other so that the forward range pressure PD can be output from the forward output port 51d.
- the pressure input port 51h communicates and the forward range pressure PD or the reverse range pressure PR can be output from the common output port 51g, and the reverse output port 51j and the reverse range pressure input port 51k communicate to each other and the reverse output port 51j. Therefore, the reverse range pressure PR can be output.
- the forward range pressure PD or the reverse range pressure PR respectively output from the forward output port 51d, the common output port 51g, and the reverse output port 51j corresponding to the fail pressure output port of the present invention is the linear range.
- a reverse pressure is input to any one of the solenoid valves SL1, SL2, SL3, and SL6, and the hydraulic pressure corresponds to the predetermined hydraulic pressure of the present invention.
- the hydraulic control device 50 includes a drain check valve (first check valve) 61, a delay check valve (second check valve) 62, an orifice ( Delay means) 63.
- the drain check valve 61 communicates and blocks the first input port 61a that communicates with the drain port 66 of the linear solenoid valve SL1, the first drain port 61b, and the first input port 61a and the first drain port 61b.
- Sealing member (first movable member) 61p, back side port 61c communicating with the back side of sealing member 61p, first input port 61a and first drain port 61b are shut off.
- a spring (first urging means) 61s that urges the sealing member 61p is provided.
- the delay check valve 62 includes a second input port 62a that communicates with the forward output port 51d, an output port 62b that communicates with the drain port 66 of the linear solenoid valve SL1, and the second input port 62a and the output port 62b.
- a sealing member (second movable member) 62p capable of switching between communication and blocking and a spring (second urging means) 62s are provided.
- the spring 62s urges the sealing member 62p so as to shut off the second input port 62a and the output port 62b, and at the second input port with a hydraulic pressure lower than the forward range pressure PD which is a predetermined hydraulic pressure.
- the output port is set to communicate with each other. Therefore, when the forward range pressure PD is input to the second input port 62a, the sealing member 62p is switched against the spring 62s so that the second input port 62a and the output port 62b communicate with each other. Become.
- the linear solenoid valve SL1, the drain check valve 61, the delay check valve 62, and the fail-safe valve 51 include a first oil passage a1, a second oil passage a2, and a third oil passage a3. It is connected.
- the first oil passage a1 connects the drain port 66 of the linear solenoid valve SL1 and the first input port 61a.
- the second oil passage a2 connects the forward output port 51d and the back port 61c, and supplies the forward range pressure PD to the drain check valve 61 from the forward output port 51d. That is, the forward output port 51d of the failsafe valve 51 is connected to the back port 61c so as to block the first input port 61a and the first drain port 61b with respect to the sealing member 61p.
- the forward range pressure PD which is a predetermined hydraulic pressure to be energized, can be output.
- the third oil passage a3 branches from the second oil passage a2, and is connected to the first oil passage a1 via the delay check valve 62.
- the orifice 63 delays the rise in the oil pressure of the first oil passage a1. Is provided.
- drain check valve 61 the drain check valve 61, the delay check valve 62, and the orifice 63 connected to the linear solenoid valve SL1 have been described.
- the drain check valve connected to the linear solenoid valve SL2 is described.
- delay check valve 72, orifice 73, drain check valve 81 connected to linear solenoid valve SL3, delay check valve 82, orifice 83, drain check valve 91 connected to linear solenoid valve SL6, delay A check valve 92 and an orifice 93 are provided.
- the drain check valves 71, 81, 91, the delay check valves 72, 82, 92, and the orifices 73, 83, 93 are composed of a drain check valve 61, a delay check valve 62, an orifice 63, respectively. Since it is the same, detailed description is abbreviate
- the fail pressure output port is the common output port 51g, and the predetermined hydraulic pressure is the forward range pressure PD or the reverse range pressure PR.
- the fail pressure output port is the reverse output port 51j, and the predetermined hydraulic pressure is in the reverse range pressure PR.
- the fail safe valve 51 When the linear solenoid valves SL1 to SL6 are operating normally, the fail safe valve 51 is in the normal position. As shown in FIG. 4, when the manual valve 52 is in the forward range, the forward range pressure PD is supplied to the fail safe valve 51, but the forward range pressure input port 51e and the original pressure input port 51h are both shut off. Therefore, the operation by the fail safe valve 51 does not occur. Further, three of the linear solenoid valves SL1 to SL6, for example, the linear solenoid valves SL1, SL2, and SL3 are operated, and the first clutch C1, the second clutch C2, and the third clutch C3 are simultaneously engaged to move forward. A rapid stage is formed.
- the reverse range pressure PR is supplied to the fail-safe valve 51.
- the reverse range pressure input port 51k and the original pressure input port 51h are both blocked, the operation by the fail safe valve 51 does not occur.
- three of the linear solenoid valves SL1 to SL6, for example, the linear solenoid valves SL2, SL3, and SL6 are operated, and the second clutch C2, the third clutch C3, and the second brake B2 are simultaneously engaged, thereby causing the reverse gear. Is formed.
- the forward range pressure PD is formed, input to the forward range pressure input port 51e, and output from the forward output port 51d.
- the forward range pressure PD output from the forward output port 51d is supplied to the back pressure port 61c of the drain check valve 61 via the second oil passage a2.
- the drain check valve 61 is locked in a state where the first port 61c and the first drain port 61b are shut off.
- the forward range pressure PD of the second oil passage a2 branches to the third oil passage a3 and is input to the second input port 62a of the delay check valve 62.
- the forward range pressure PD pushes the sealing member 62p against the urging force of the spring 62s, the second input port 62a and the output port 62b are communicated, and hydraulic pressure is output from the output port 62b.
- the forward range pressure PD passes through the delay check valve 62, the forward range pressure PD is delayed and reduced in order to switch the sealing member 62p to the open side.
- the hydraulic oil flowing through the third oil passage a3 causes a delay in the rise and supply of the hydraulic pressure. Therefore, after the forward range pressure PD locks the drain check valve 61 to the shut-off side, the first oil passage The drain check valve 61 is reached within a1. Moreover, since the hydraulic pressure of the hydraulic oil flowing through the third oil passage a3 is reduced, when the hydraulic pressure from the first oil passage a1 reaches the drain check valve 61, the lock pressure and the lock of the spring 61s are locked. Since the resultant force is smaller than the resultant force, the hydraulic pressure from the first oil passage a1 cannot open the drain check valve 61, and the hydraulic oil flows into the drain port 66 of the linear solenoid valve SL1 and is turned off. The hydraulic servo 60 is operated by being output from the output port 65 that communicates by fail.
- the forward range pressure PD is output from the output port 53c, input to the original pressure input port 51h, and output from the common output port 51g.
- the forward range pressure PD output from the common output port 51g is supplied to the drain port 76 of the linear solenoid valve SL2 and the drain port 86 of the linear solenoid valve SL3 to operate the hydraulic servos 70 and 80.
- a drain check valve 71, a delay check valve 72, and an orifice 73 are interposed between the common output port 51g and the drain port 76 of the linear solenoid valve SL2, and the common output port 51g Between the drain port 86 of the linear solenoid valve SL3, a drain check valve 81, a delay check valve 82, and an orifice 83 are interposed, all of which are the drain check valve 61 and the delay check described above. Since the configuration and operation are the same as those of the valve 62 and the orifice 63, description thereof will be omitted.
- the failsafe valve 51 is switched to the fail position as the limp home function, and when the manual valve 52 is in the forward range, the hydraulic servos 60, 70, By operating 80, the first clutch C1, the second clutch C2, and the third clutch C3 are simultaneously engaged to form the seventh forward speed.
- the reverse range pressure PR is formed, input to the reverse range pressure input port 51k, and output from the reverse output port 51j.
- the reverse range pressure PR output from the reverse output port 51j is supplied to the drain port 96 of the linear solenoid valve SL6 to operate the hydraulic servo 90.
- a drain check valve 91, a delay check valve 92, and an orifice 93 are interposed between the reverse output port 51j and the drain port 96 of the linear solenoid valve SL6.
- 61, the delay check valve 62, and the orifice 63 have the same configuration and operation, and thus the description thereof is omitted.
- the reverse range pressure PR is output from the output port 53c, input to the original pressure input port 51h, and output from the common output port 51g.
- the reverse range pressure PR output from the common output port 51g is supplied to the drain port 76 of the linear solenoid valve SL2 and the drain port 86 of the linear solenoid valve SL3 to operate the hydraulic servos 70 and 80.
- the failsafe valve 51 is switched to the fail position as the limp home function, and when the manual valve 52 is in the reverse range, the hydraulic servos 70, 80, When 90 is operated, the second clutch C2, the third clutch C3, and the second brake B2 are simultaneously engaged, and a reverse gear is formed.
- the linear solenoid valves SL1, SL2, SL3, SL6 and the drain check valves 61, 71, 81, 91 are in direct communication. Therefore, the linear solenoid valves SL1, SL2, SL3, SL6 and the drain check valves 61, 71, 81, 91 are communicated with each other as compared with the case where the drain check valve is communicated via the fail safe valve 51.
- the first oil passage a1 can be shortened, and a decrease in controllability due to an increase in flow resistance and an increase in size of the hydraulic control device can be suppressed.
- the sealing member 61p of the drain check valve 61 is output from the forward output port 51d of the fail safe valve 51 at the time of failure when the linear solenoid valve SL1 is de-energized. Due to the forward range pressure PD, the first input port 61a and the first drain port 61b are energized so as to be shut off.
- the hydraulic pressure that has passed through the delay check valve 62 reaches the side of the drain check valve 61 that opens the first input port 61a, but the hydraulic pressure is supplied when the delay check valve 62 switches to the open side.
- the rise is delayed, and when the hydraulic pressure reaches the drain check valve 61, the cutoff of the first input port 61a and the first drain port 61b is already locked.
- the lock pressure is the forward range pressure PD. And it is smaller than the locking force of the spring 61s.
- the hydraulic pressure output from the delay check valve 62 is reversely input to the drain port 66 of the linear solenoid valve SL1 without opening the drain check valve 61, and is supplied to the hydraulic servo 60 to be controllable. be able to.
- the other drain check valves 71, 81, 91 have the same operational effects as the drain check valve 61, and thus detailed description thereof is omitted.
- the drain check valve 61 is connected to the first oil passage a1 that connects the drain port 66 of the linear solenoid valve SL1 and the first input port 61a, and the forward output port 51d.
- the orifice 63 that delays the rise in the hydraulic pressure of the first oil passage a1 is provided in the third oil passage a3.
- the hydraulic pressure supplied from the delay check valve 62 to the drain check valve 61 when the fail safe valve 51 is switched to the fail position can be further delayed.
- the hydraulic pressure from the delay check valve 62 reaches after the shutoff of the first input port 61a and the first drain port 61b is more reliably locked, and is more stable. Operation can be realized.
- the delay means is the orifice 63 interposed in the third oil passage a3. Therefore, the configuration can be simplified and the cost of parts is increased. Can be suppressed as much as possible.
- the hydraulic control device 50 of the present embodiment includes a normally open type solenoid valve SR that supplies hydraulic pressure to the fail safe valve 51 and switches the fail safe valve 51 to the fail position at the time of failure. For this reason, during all-off failure, the hydraulic pressure is supplied from the solenoid valve SR to the first oil chamber 51a of the fail-safe valve 51. Therefore, the spool 51p is pushed downward against the spring 51s, and the fail-safe valve 51 is normal. Switch from position to fail position.
- the first clutch C1, the second clutch C2, and the third clutch C3 are selected as the three engagement elements for forming the seventh forward speed.
- the second clutch C2, the third clutch C3, and the fourth clutch C4 may be selected.
- a linear solenoid valve SL4 is applied instead of the linear solenoid valve SL1 shown in FIGS.
- the shift speed formed at the time of limp home in the forward range is not limited to the above embodiment, and other shift speeds may be formed.
- the present invention is not limited to this, and any member or mechanism that delays the increase or supply of the hydraulic pressure is applied as appropriate. be able to.
- the forward range pressure PD or the reverse range pressure PR is supplied as the lock pressure to the sealing member 61p of the drain check valve 61 at the time of all-off failure.
- a hydraulic pressure other than the forward range pressure PD and the reverse range pressure PR is supplied as a lock pressure to the sealing member 61p of the drain check valve 61, for example, a hydraulic pressure from a separately provided solenoid valve, etc.
- a mechanical external force such as a member or mechanism other than hydraulic pressure may be applied.
- the hydraulic control device 50 selectively engages three engagement elements among the first clutch C1 to the fourth clutch C4, the first brake B1, and the second brake B2, thereby providing a plurality of engagements.
- the first clutch C1 to the third clutch C3 that form a predetermined forward speed (seventh forward speed) and the second clutch C2 the third clutch C3, and the second clutch that form the reverse speed.
- the first clutch C1 to the fourth clutch C4 the first brake B1 and A plurality of linear solenoid valves SL1, SL2, SL3, SL6 capable of supplying hydraulic pressure to the hydraulic servos 60, 70, 80, 90 of the second brake B2, and forward range pressure PD or
- the hydraulic pressure can be supplied to the hydraulic servo 60 of the first clutch C1 other than the second clutch C2 and the third clutch C3, which are some of the engaging elements of the first clutch C1 to the third clutch C3 forming the forward gear.
- the forward output port 51d communicated with the drain port 66 of the linear solenoid valve SL1 and the second clutch C2, which forms the reverse gear
- the drain of the linear solenoid valve SL6 capable of supplying hydraulic pressure to the hydraulic servo 90 of the second brake B2 other than the second clutch C2 and the third clutch C3, which are part of the engagement elements of the third clutch C3 and the second brake B2.
- a reverse output port 51j communicated with the port 96, a normal position where all of the common output port 51g, the forward output port 51d and the reverse output port 51j are drained, and the original pressure input port 51h
- the common output port 51g communicates
- the forward range pressure input port 51e communicates with the forward output port 51d
- the fail position can communicate with the reverse range pressure input port 51k and the reverse output port 51j.
- a fail-safe valve 51 is
- the fail safe valve 51 when the linear solenoid valves SL1 to SL6 all fail, the fail safe valve 51 is switched to the fail position, so that either the seventh forward speed or the reverse speed is selected.
- the limp home function can be realized by selecting. Further, since the fail-safe valve 51 necessary for the limp home function can be realized with only one switching valve, the number of parts can be reduced compared with the case where a plurality of switching valves are used, and the hydraulic control device 50 can be reduced in size. Can be achieved.
- the input port of the fail safe valve 51 includes three input ports: a forward range pressure input port 51e, a source pressure input port 51h, and a reverse range pressure input port 51k.
- the output port includes three output ports: a forward output port 51d, a common output port 51g, and a reverse output port 51j. For this reason, the full length of the fail safe valve 51 can be shortened and size reduction can be achieved.
- the hydraulic control device 50 outputs the forward range pressure PD when the shift speed is the forward speed, and outputs the reverse range pressure PR when the shift speed is the reverse speed.
- An output mechanism 52 and a three-way valve (selection mechanism) 53 that inputs the output one of the forward range pressure PD and the reverse range pressure PR as a source pressure to the source pressure input port 51h are provided.
- the three-way valve 53 inputs the output one of the forward range pressure PD and the reverse range pressure PR as the source pressure to the source pressure input port 51h.
- the original pressure can be generated from the forward range pressure PD and the reverse range pressure PR, and an increase in parts cost and an increase in the size of the hydraulic control device can be suppressed.
- the range pressure output mechanism is a manual valve 52.
- the source pressure is either the forward range pressure PD or the reverse range pressure PR output via the manual valve 52, so that the neutral is selected by the shift lever. If it is, the source pressure is not output. For this reason, the fail-safe valve 51 is in a fail position due to a failure of a valve stick or the like, and an on-fail occurs in a solenoid valve other than the solenoid valve communicated with the common output port 51g. Even if a double failure occurs, if the neutral is selected by the shift lever, the hydraulic pressure is not supplied to the solenoid valve connected to the common output port 51g, so the neutral is selected. In this case, it is possible to prevent any of the forward gear and the reverse gear from being formed.
- the second clutch C2 and the third clutch C3, which are some engagement elements, are two engagement elements. Therefore, there are two linear solenoid valves SL2 and SL3 communicated with the common output port 51g, and one linear solenoid valve SL1 and SL6 respectively communicated with the forward output port 51d and the reverse output port 51j. become. For this reason, for example, when the driver switches the shift lever from the D range to the R range during an all-off failure, only one of the three engagement elements is switched to supply the hydraulic pressure, and the forward gear or the reverse gear is switched. Switching can be performed quickly.
- the branching point of the oil passage between the failsafe valve 51 and the linear solenoid valves SL2 and SL3 can be suppressed to only one point, for example, a common part of the engaging elements can be used as one forward stage or Compared with the case where there are two branch points for each of the other two engaging elements engaged in the reverse gear, the hydraulic flow rate loss can be reduced and the hydraulic circuit can be made compact. .
- the six engaging elements are the four clutches of the first clutch C1 to the fourth clutch C4 and the two brakes of the first brake B1 and the second brake B2,
- the first clutch C1 to the third clutch C3 that form the gears are three clutches that form the direct-coupled gear among the four clutches of the first clutch C1 to the fourth clutch C4.
- the hydraulic control device of the automatic transmission can be used for vehicles such as passenger cars and trucks, and in particular, has a limp home function for off-fail of a solenoid valve capable of supplying hydraulic pressure to a hydraulic servo of a plurality of engagement elements. It is suitable for use in what it has.
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Abstract
Description
前記係合要素(C1)の油圧サーボ(60)に油圧を供給可能なノーマルクローズタイプの第1のソレノイドバルブ(SL1)と、
前記第1のソレノイドバルブ(SL1)のドレーンポート(66)に連通する第1の入力ポート(61a)と、第1のドレーンポート(61b)と、前記第1の入力ポート(61a)及び前記第1のドレーンポート(61b)の連通及び遮断を切換可能な第1の可動部材(61p)と、前記第1の入力ポート(61a)及び前記第1のドレーンポート(61b)を遮断するように前記第1の可動部材(61p)に付勢する第1の付勢手段(61s)と、を有する第1のチェックバルブ(61)と、
前記第1のソレノイドバルブ(SL1)が非通電となるフェール時にフェール位置に切り換わると共に、所定の油圧(PD,PR)を出力するフェール圧出力ポート(51d,51g,51j)を有するフェールセーフバルブ(51)と、
前記フェール圧出力ポート(51d,51g,51j)に連通する第2の入力ポート(62a)と、前記第1のソレノイドバルブ(SL1)の前記ドレーンポート(66)及び前記第1のチェックバルブ(61)の前記第1の入力ポート(61a)に連通する出力ポート(62b)と、前記第2の入力ポート(62a)及び前記出力ポート(62b)の連通及び遮断を切換可能な第2の可動部材(62p)と、前記第2の入力ポート(62a)及び前記出力ポート(62b)を遮断するように前記第2の可動部材(62p)に付勢すると共に、前記所定の油圧(PD,PR)より低い油圧で前記第2の入力ポート(62a)及び前記出力ポート(62b)を連通させる第2の付勢手段(62s)と、を有する第2のチェックバルブ(62)と、を備え、
前記第1のチェックバルブ(61)の前記第1の可動部材(61p)は、前記第1のソレノイドバルブ(SL1)が非通電となる前記フェール時に、前記第1の入力ポート(61a)及び前記第1のドレーンポート(61b)を遮断するように付勢されることを特徴とする。
50 油圧制御装置
51 フェールセーフバルブ
51d 前進用出力ポート(フェール圧出力ポート)
51g 共通用出力ポート(フェール圧出力ポート)
51j 後進用出力ポート(フェール圧出力ポート)
60 油圧サーボ
61 ドレーンチェックバルブ(第1のチェックバルブ)
61a 第1の入力ポート
61b 第1のドレーンポート
61p 封止部材(第1の可動部材)
61s スプリング(第1の付勢手段)
62 遅延用チェックバルブ(第2のチェックバルブ)
62a 第2の入力ポート
62b 出力ポート
62p 封止部材(第2の可動部材)
62s スプリング(第2の付勢手段)
63 オリフィス(遅延手段)
66 ドレーンポート
71 ドレーンチェックバルブ(第1のチェックバルブ)
72 遅延用チェックバルブ(第2のチェックバルブ)
73 オリフィス(遅延手段)
81 ドレーンチェックバルブ(第1のチェックバルブ)
82 遅延用チェックバルブ(第2のチェックバルブ)
83 オリフィス(遅延手段)
91 ドレーンチェックバルブ(第1のチェックバルブ)
92 遅延用チェックバルブ(第2のチェックバルブ)
93 オリフィス(遅延手段)
a1 第1の油路
a2 第2の油路
a3 第3の油路
C1 第1クラッチ(係合要素)
PD 前進レンジ圧(所定の油圧)
PR 後進レンジ圧(所定の油圧)
SL1 リニアソレノイドバルブ(第1のソレノイドバルブ)
SR ソレノイドバルブ(第2のソレノイドバルブ)
Claims (5)
- 複数の係合要素を選択的に係合することで複数の変速段を形成可能な自動変速機の油圧制御装置において、
前記係合要素の油圧サーボに油圧を供給可能なノーマルクローズタイプの第1のソレノイドバルブと、
前記第1のソレノイドバルブのドレーンポートに連通する第1の入力ポートと、第1のドレーンポートと、前記第1の入力ポート及び前記第1のドレーンポートの連通及び遮断を切換可能な第1の可動部材と、前記第1の入力ポート及び前記第1のドレーンポートを遮断するように前記第1の可動部材に付勢する第1の付勢手段と、を有する第1のチェックバルブと、
前記第1のソレノイドバルブが非通電となるフェール時にフェール位置に切り換わると共に、所定の油圧を出力するフェール圧出力ポートを有するフェールセーフバルブと、
前記フェール圧出力ポートに連通する第2の入力ポートと、前記第1のソレノイドバルブの前記ドレーンポート及び前記第1のチェックバルブの前記第1の入力ポートに連通する出力ポートと、前記第2の入力ポート及び前記出力ポートの連通及び遮断を切換可能な第2の可動部材と、前記第2の入力ポート及び前記出力ポートを遮断するように前記第2の可動部材に付勢すると共に、前記所定の油圧より低い油圧で前記第2の入力ポート及び前記出力ポートを連通させる第2の付勢手段と、を有する第2のチェックバルブと、を備え、
前記第1のチェックバルブの前記第1の可動部材は、前記第1のソレノイドバルブが非通電となる前記フェール時に、前記第1の入力ポート及び前記第1のドレーンポートを遮断するように付勢される、
ことを特徴とする自動変速機の油圧制御装置。 - 前記第1のチェックバルブの前記第1の可動部材は、前記第1のソレノイドバルブが非通電となる前記フェール時に、前記フェールセーフバルブの前記フェール圧出力ポートから出力された前記所定の油圧により、前記第1の入力ポート及び前記第1のドレーンポートを遮断するように付勢される、
ことを特徴とする請求項1記載の自動変速機の油圧制御装置。 - 前記第1のソレノイドバルブの前記ドレーンポートと前記第1の入力ポートとを接続する第1の油路と、
前記フェール圧出力ポートから前記第1のチェックバルブに前記所定の油圧を供給させる第2の油路と、
前記第2の油路から分岐し、前記第2のチェックバルブを介して前記第1の油路に接続する第3の油路と、を備え、
前記第3の油路を介して前記第1の油路へ油圧を供給する際に、当該第1の油路の油圧の上昇を遅延させる遅延手段を前記第3の油路に備える、
ことを特徴とする請求項2記載の自動変速機の油圧制御装置。 - 前記遅延手段は、前記第3の油路に設けられたオリフィスである、
ことを特徴とする請求項3記載の自動変速機の油圧制御装置。 - 前記フェール時に、前記フェールセーフバルブに油圧を供給すると共に、前記フェールセーフバルブを前記フェール位置に切り換えるノーマルオープンタイプの第2のソレノイドバルブを備える、
ことを特徴とする請求項1乃至4のいずれか1項に記載の自動変速機の油圧制御装置。
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CN201480069590.1A CN105829775B (zh) | 2013-12-26 | 2014-12-24 | 自动变速器的油压控制装置 |
US15/100,794 US9759315B2 (en) | 2013-12-26 | 2014-12-24 | Hydraulic control device for automatic transmission |
DE112014004908.5T DE112014004908B4 (de) | 2013-12-26 | 2014-12-24 | Hydrauliksteuerungsvorrichtung für Automatikgetriebe |
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JP2013270425A JP6131852B2 (ja) | 2013-12-26 | 2013-12-26 | 自動変速機の油圧制御装置 |
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US10837503B2 (en) * | 2015-11-26 | 2020-11-17 | Isuzu Motors Limited | Hydraulic-oil control device |
Citations (4)
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JPH07217731A (ja) * | 1994-01-31 | 1995-08-15 | Mitsubishi Automob Eng Co Ltd | 自動変速機の油圧回路 |
JP2009085351A (ja) * | 2007-09-28 | 2009-04-23 | Aisin Aw Co Ltd | 自動変速機の油圧制御装置 |
JP2009150532A (ja) * | 2007-11-30 | 2009-07-09 | Aisin Aw Co Ltd | 自動変速機の油圧制御装置 |
JP2010236668A (ja) * | 2009-03-31 | 2010-10-21 | Aisin Aw Co Ltd | 自動変速機の油圧制御装置 |
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US6164734A (en) * | 1997-03-14 | 2000-12-26 | Toyota Jidosha Kabushiki Kaisha | Vehicle hydraulic braking system having reservoir for storing fluid discharged from brake cylinder through pressure control valve device |
KR100387509B1 (ko) * | 2001-08-21 | 2003-06-18 | 현대자동차주식회사 | 차량용 자동 변속기의 유압 제어시스템 |
JP4490172B2 (ja) | 2004-05-31 | 2010-06-23 | トヨタ自動車株式会社 | 車両用自動変速機の油圧制御装置 |
US8316630B2 (en) * | 2008-08-27 | 2012-11-27 | Honeywell International Inc. | Flow equalizing override assembly for fuel divider system |
JP5549565B2 (ja) * | 2010-12-03 | 2014-07-16 | アイシン・エィ・ダブリュ株式会社 | 動力伝達装置 |
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Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07217731A (ja) * | 1994-01-31 | 1995-08-15 | Mitsubishi Automob Eng Co Ltd | 自動変速機の油圧回路 |
JP2009085351A (ja) * | 2007-09-28 | 2009-04-23 | Aisin Aw Co Ltd | 自動変速機の油圧制御装置 |
JP2009150532A (ja) * | 2007-11-30 | 2009-07-09 | Aisin Aw Co Ltd | 自動変速機の油圧制御装置 |
JP2010236668A (ja) * | 2009-03-31 | 2010-10-21 | Aisin Aw Co Ltd | 自動変速機の油圧制御装置 |
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DE112014004908B4 (de) | 2022-05-12 |
US9759315B2 (en) | 2017-09-12 |
JP6131852B2 (ja) | 2017-05-24 |
DE112014004908T5 (de) | 2016-07-21 |
CN105829775A (zh) | 2016-08-03 |
CN105829775B (zh) | 2017-07-04 |
JP2015124842A (ja) | 2015-07-06 |
US20160305543A1 (en) | 2016-10-20 |
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