JP5018521B2 - Hydraulic control device for automatic transmission - Google Patents

Description

  The present invention relates to a hydraulic control device for an automatic transmission, and more particularly, to a hydraulic control device in which hydraulic oil flowing out from a first control mechanism (primary regulator valve) is supplied to a second control mechanism (secondary regulator valve).

  Conventionally, there is a vehicle in which a fluid coupling such as a torque converter is provided between a drive source and an automatic transmission. Some torque converters include a lock-up clutch that directly connects an input shaft and an output shaft of the torque converter. The hydraulic pressure (hydraulic oil pressure) supplied to the lockup clutch is adjusted (controlled) by the secondary regulator valve. The hydraulic oil flowing out from the primary regulator valve is supplied to the secondary regulator valve.

  By the way, when the amount of oil returning from the hydraulic circuit to the oil pan increases with respect to the amount of oil discharged from the oil pump, there may be a shortage of working oil flowing to the secondary regulator valve via the primary regulator valve. In this case, there is a possibility that the state of the lockup clutch cannot be controlled. Therefore, in order to secure the hydraulic oil supplied to the secondary regulator valve (lockup clutch), an oil passage is provided for bypassing the primary regulator valve and supplying the hydraulic oil directly from the oil pump to the secondary regulator valve.

  A hydraulic control circuit described in Japanese Patent Application Laid-Open No. 2003-90424 (Patent Document 1) adjusts a first line oil passage into which hydraulic oil pumped from an oil pan by an oil pump flows, and a hydraulic pressure in the first line oil passage. A primary regulator valve, a second line oil passage through which excess hydraulic oil that has flowed out of the primary regulator valve flows, a secondary regulator valve that adjusts the hydraulic pressure in the second line oil passage, and the hydraulic pressure adjusted by the secondary regulator valve A torque converter to which the lockup clutch is engaged or released by being supplied, and a bypass oil passage that is branched from the first line oil passage and distributes part of the hydraulic oil to the second line oil passage; including.

According to the hydraulic control circuit described in this publication, the hydraulic oil discharged from the oil pump is supplied to the torque converter through the second line oil passage without passing through the primary regulator valve by the bypass passage. Thereby, hydraulic fluid can fully be supplied to the 2nd line oil way. Therefore, engagement of the lockup clutch due to lack of hydraulic oil can be suppressed. As a result, the lockup clutch can be prevented from being dragged.
JP 2003-90424 A

  However, when a bypass oil passage that bypasses the primary regulator valve is provided as in the hydraulic control circuit described in Japanese Patent Application Laid-Open No. 2003-90424, when hydraulic pressure is directly supplied to the secondary regulator valve via the bypass oil passage. In addition, the line pressure can be reduced. Therefore, the hydraulic pressure required for the operation of the friction engagement elements (such as clutches and brakes) of the automatic transmission may be insufficient.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a hydraulic control device for an automatic transmission that can reduce the amount of decrease in hydraulic pressure.

  A hydraulic control device for an automatic transmission according to a first aspect of the invention is a hydraulic control device for an automatic transmission that is operated by the pressure of hydraulic oil. The hydraulic control device includes a first storage unit that stores hydraulic oil, a first oil passage that is supplied with hydraulic oil stored in the first storage unit by a supply mechanism, and an operation of the first oil passage. A first control mechanism that controls the pressure of the oil, a second oil passage that is supplied with hydraulic oil that has flowed out of the first control mechanism, and a second control that controls the pressure of the hydraulic oil in the second oil passage. A control mechanism, a third oil path connected to at least one of the first oil path and the second oil path, and a second oil path connected to the third oil path and storing hydraulic oil. A storage unit, and a switching mechanism that switches between a state in which the third oil passage and the second storage unit are communicated with each other, and a state in which the third storage unit is shut off.

  According to this structure, the hydraulic oil stored in the 1st storage part (for example, oil pan) is supplied to a 1st oil path. The pressure of the hydraulic oil in the first oil passage is controlled by a first control mechanism (for example, a primary regulator valve). The hydraulic oil that has flowed out of the first control mechanism is supplied to the second oil passage. The pressure of the hydraulic oil in the second oil passage is controlled by a second control mechanism (for example, a secondary regulator valve). A third oil passage is connected to at least one of the first oil passage and the second oil passage. A second storage unit that stores hydraulic oil is connected to the third oil passage. A state where the third oil passage and the second storage unit are communicated and a state where they are shut off are switched by the switching mechanism. Thereby, when the flow rate of the hydraulic oil in the first oil passage or the second oil passage is sufficient, the hydraulic oil can be stored in the second storage unit. When the flow rate of the hydraulic oil in the first oil passage or the second oil passage is insufficient, the hydraulic oil stored in the second storage section is supplied to the first oil passage or the second oil passage. Can do. Since the hydraulic oil is supplied from the second storage unit provided separately from the first oil passage and the second oil passage, without reducing the oil pressure of the first oil passage and the second oil passage, Insufficient hydraulic fluid flow can be compensated. As a result, it is possible to provide a hydraulic control device for an automatic transmission that can reduce the amount of decrease in hydraulic pressure.

  In the hydraulic control device for an automatic transmission according to the second invention, in addition to the configuration of the first invention, the switching mechanism operates in a state in which the third oil passage and the second storage unit are communicated with each other and a state in which the second storage unit is shut off. Switch according to the oil temperature.

  According to this structure, the state which connected the 3rd oil path and the 2nd storage part, and the state which interrupted | blocked according to the temperature of hydraulic fluid are switched. Accordingly, it is accurately determined from the temperature of the hydraulic oil whether the flow rate of the hydraulic oil is sufficient or can be insufficient, and if the flow rate of the hydraulic oil can be insufficient, the second storage unit A 3rd oil path and a 2nd storage part can be connected so that the stored hydraulic fluid may be supplied to a 1st oil path or a 2nd oil path.

  In the hydraulic control device for an automatic transmission according to the third invention, in addition to the configuration of the first or second invention, the third oil passage is connected to the first oil passage.

  According to this configuration, by supplying the hydraulic oil stored in the second storage unit to the first oil passage, it is possible to compensate for the insufficient flow rate of the hydraulic oil.

  In the hydraulic control apparatus for an automatic transmission according to the fourth aspect of the invention, in addition to the configuration of the first or second aspect, the third oil passage uses hydraulic oil in the first oil passage as a first control mechanism. Is connected to the first oil passage and the second oil passage so as to be supplied to the second oil passage.

  According to this structure, the hydraulic fluid shortage of hydraulic fluid can be compensated by supplying the hydraulic fluid stored in the 2nd storage part to the 2nd oil passage.

  The hydraulic control device for an automatic transmission according to a fifth aspect of the present invention is configured such that, in addition to the configuration of the first or second aspect, the pressure is controlled by at least one of the first control mechanism and the second control mechanism. An operation mechanism that operates when supplied with the controlled hydraulic oil is further provided. The third oil passage is connected to the second oil passage so as to supply at least one of the hydraulic oil discharged from the operation mechanism and the hydraulic oil leaked from the operation mechanism to the second oil passage. Connected.

  According to this configuration, the working oil supplied from the first control mechanism or the second control mechanism to the working mechanism can be returned to the second oil passage. For this reason, it is possible to compensate for the shortage of the flow rate of the hydraulic oil without increasing the flow rate of the hydraulic oil.

  In the hydraulic control device for an automatic transmission according to the sixth aspect of the invention, in addition to the configuration of any one of the first to fifth aspects, the second storage unit includes the first oil passage, the second oil passage, and the second oil passage. 3 is provided in a valve body in which three oil passages are formed.

  According to this configuration, the first oil passage, the second oil passage, the third oil passage, and the second storage portion are integrally provided in one valve body, thereby shortening the overall length of the oil passage. Can do. Therefore, it is possible to reduce the resistance force when the hydraulic oil flows through the oil passage.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same parts are denoted by the same reference numerals. Their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

<First Embodiment>
A vehicle equipped with a hydraulic control apparatus according to a first embodiment of the present invention will be described with reference to FIG. This vehicle is an FF (Front engine Front drive) vehicle. The vehicle may be a vehicle other than FF.

  The vehicle includes an engine 1000, an automatic transmission 2000, a planetary gear unit 3000 that forms part of the automatic transmission 2000, a valve body 4000 that forms part of the automatic transmission 2000, a differential gear 5000, a drive shaft 6000, Front wheel 7000 and ECU (Electronic Control Unit) 8000 are included.

  Engine 1000 is an internal combustion engine that burns a mixture of fuel and air injected from an injector (not shown) in a combustion chamber of a cylinder. The piston in the cylinder is pushed down by the combustion, and the crankshaft is rotated. An external combustion engine may be used instead of the internal combustion engine. Further, a rotating electrical machine or the like may be used instead of the engine 1000.

  Automatic transmission 2000 changes the rotational speed of the crankshaft to a desired rotational speed by forming a desired gear stage. The output gear of automatic transmission 2000 is meshed with differential gear 5000.

  A drive shaft 6000 is connected to the differential gear 5000 by spline fitting or the like. Power is transmitted to the left and right front wheels 7000 via the drive shaft 6000.

  The ECU 8000 includes a vehicle speed sensor 8002, a position switch 8005 of a shift lever 8004, an accelerator opening sensor 8007 of an accelerator pedal 8006, a stop lamp switch 8009 provided on a brake pedal 8008, an oil temperature sensor 8010, an input shaft. A rotational speed sensor 8012, an output shaft rotational speed sensor 8014, and a water temperature sensor 8016 are connected via a harness or the like.

  The vehicle speed sensor 8002 detects the vehicle speed of the vehicle from the rotational speed of the drive shaft 6000, and transmits a signal representing the detection result to the ECU 8000. The position of shift lever 8004 is detected by position switch 8005, and a signal representing the detection result is transmitted to ECU 8000. Corresponding to the position of the shift lever 8004, the gear stage of the automatic transmission 2000 is automatically formed. Further, a manual shift mode in which the driver can select an arbitrary gear stage may be selected according to the driver's operation.

  The accelerator opening sensor 8007 detects the opening of the accelerator pedal 8006 and transmits a signal representing the detection result to the ECU 8000. A stop lamp switch 8009 detects the ON / OFF state of the brake pedal 8008 and transmits a signal representing the detection result to the ECU 8000. A stroke sensor for detecting the stroke amount of the brake pedal 8008 may be provided instead of or in addition to the stop lamp switch 8009.

  Oil temperature sensor 8010 detects the temperature of an automatic transmission fluid (ATF) of automatic transmission 2000 and transmits a signal representing the detection result to ECU 8000.

  Input shaft speed sensor 8012 detects input shaft speed NI of automatic transmission 2000 and transmits a signal representing the detection result to ECU 8000. Output shaft rotational speed sensor 8014 detects output shaft rotational speed NO of automatic transmission 2000 and transmits a signal representing the detection result to ECU 8000. Water temperature sensor 8016 detects the temperature of the cooling water temperature of engine 1000 and transmits a signal representing the detection result to ECU 8000.

  ECU 8000 includes signals sent from vehicle speed sensor 8002, position switch 8005, accelerator opening sensor 8007, stop lamp switch 8009, oil temperature sensor 8010, input shaft speed sensor 8012, output shaft speed sensor 8014, ROM ( Based on the map and program stored in the Read Only Memory), the devices are controlled so that the vehicle is in a desired running state.

  The planetary gear unit 3000 will be described with reference to FIG. Planetary gear unit 3000 is connected to a torque converter 3200 having an input shaft 3100 coupled to a crankshaft. Planetary gear unit 3000 includes first set 3300 of planetary gear mechanisms, second set 3400 of planetary gear mechanisms, output gear 3500, B1 brake 3610, B2 brake 3620 and B3 brake 3630 fixed to gear case 3600, and C1. Clutch 3640 and C2 clutch 3650, and one-way clutch F3660 are included.

  The first set 3300 is a single pinion type planetary gear mechanism. First set 3300 includes sun gear S (UD) 3310, pinion gear 3320, ring gear R (UD) 3330, and carrier C (UD) 3340.

  Sun gear S (UD) 3310 is coupled to output shaft 3210 of torque converter 3200. Pinion gear 3320 is rotatably supported by carrier C (UD) 3340. Pinion gear 3320 is engaged with sun gear S (UD) 3310 and ring gear R (UD) 3330.

  Ring gear R (UD) 3330 is fixed to gear case 3600 by B3 brake 3630. Carrier C (UD) 3340 is fixed to gear case 3600 by B1 brake 3610.

  The second set 3400 is a Ravigneaux type planetary gear mechanism. The second set 3400 includes a sun gear S (D) 3410, a short pinion gear 3420, a carrier C (1) 3422, a long pinion gear 3430, a carrier C (2) 3432, a sun gear S (S) 3440, and a ring gear R. (1) (R (2)) 3450.

  Sun gear S (D) 3410 is coupled to carrier C (UD) 3340. Short pinion gear 3420 is rotatably supported by carrier C (1) 3422. Short pinion gear 3420 is engaged with sun gear S (D) 3410 and long pinion gear 3430. Carrier C (1) 3422 is coupled to output gear 3500.

  Long pinion gear 3430 is rotatably supported by carrier C (2) 3432. Long pinion gear 3430 is engaged with short pinion gear 3420, sun gear S (S) 3440, and ring gear R (1) (R (2)) 3450. Carrier C (2) 3432 is coupled to output gear 3500.

  Sun gear S (S) 3440 is coupled to output shaft 3210 of torque converter 3200 by C1 clutch 3640. Ring gear R (1) (R (2)) 3450 is fixed to gear case 3600 by B2 brake 3620 and connected to output shaft 3210 of torque converter 3200 by C2 clutch 3650. The ring gear R (1) (R (2)) 3450 is connected to the one-way clutch F3660, and cannot rotate when the first gear is driven.

  The one-way clutch F3660 is provided in parallel with the B2 brake 3620. That is, the outer race of the one-way clutch F3660 is fixed to the gear case 3600, and the inner race is connected to the ring gear R (1) (R (2)) 3450 via the rotation shaft.

  FIG. 3 shows an operation table showing the relationship between each gear position and the operation state of each clutch and each brake. By operating each brake and each clutch with the combinations shown in this operation table, a forward gear stage of 1st to 6th speed and a reverse gear stage are formed.

  Since the one-way clutch F3660 is provided in parallel with the B2 brake 3620, as shown in the operation table, the B2 brake is applied in the driving state (acceleration) from the engine side when the first gear (1ST) is formed. There is no need to engage 3620.

  The one-way clutch F3660 restricts the rotation of the ring gear R (1) (R (2)) 3450 when the first gear is driven. When the engine brake is applied, the one-way clutch F3660 does not limit the rotation of the ring gear R (1) (R (2)) 3450.

  That is, at the time of driving in normal shift control, the first gear is formed by engaging C1 clutch 3640 and one-way clutch F3660. During engine braking in normal shift control, the first gear is established by engaging the C1 clutch 3640 and the B2 brake 3620.

  The valve body 4000 will be described with reference to FIG. FIG. 4 shows only a part of the valve body 4000 related to the present invention. A hydraulic circuit is formed in the valve body 4000. In the valve body 4000, there are a primary regulator valve 4006, a secondary regulator valve 4008, a manual valve 4100, a solenoid modulator valve 4200, an SL1 linear solenoid (hereinafter referred to as SL (1)) 4210, and an SL2 linear solenoid. (Hereinafter referred to as SL (2)) 4220, SL3 linear solenoid (hereinafter referred to as SL (3)) 4230, SL4 linear solenoid (hereinafter referred to as SL (4)) 4240, and SLT linear A solenoid (hereinafter referred to as SLT) 4300 and a B2 control valve 4500 are provided.

  Oil pressure is supplied to the hydraulic circuit formed in the valve body 4000 from an oil pump 4004 provided outside the valve body 4000. Oil pump 4004 is connected to the crankshaft of engine 1000. As the crankshaft rotates, the oil pump 4004 is driven to suck the ATF stored in the oil pan 4002 and generate hydraulic pressure. The hydraulic pressure generated by the oil pump 4004 is adjusted (controlled) by the primary regulator valve 4006 to generate line pressure (hydraulic pressure in the line pressure oil passage 4010).

  Primary regulator valve 4006 operates using the throttle pressure adjusted by SLT 4300 as a pilot pressure. The line pressure is supplied to the manual valve 4100 via the line pressure oil passage 4010. Further, the line pressure is adjusted by SL (4) 4240 and supplied to the B3 brake 3630. The line pressure oil passage 4010 is formed in the valve body 4000.

  Secondary regulator valve 4008 operates using the throttle pressure adjusted by SLT 4300 as a pilot pressure. The secondary regulator valve 4008 adjusts the hydraulic pressure in the secondary pressure oil passage 4012 into which excess hydraulic oil that has flowed out (discharged) from the primary regulator valve 4006 flows. Secondary pressure (hydraulic pressure in the secondary pressure oil passage 4012) is generated by the secondary regulator valve 4008. The ATF is supplied to the torque converter 3200 through the secondary regulator valve 4008, supplied to an oil cooler (not shown), or supplied to the lubrication path of the automatic transmission 2000. Secondary pressure oil passage 4012 is formed in valve body 4000.

  The ATF supplied to the torque converter 3200 is used to transmit power in the torque converter 3200 and to engage or disengage a lock-up clutch (not shown).

  Manual valve 4100 includes a drain port 4105. From the drain port 4105, the oil pressure in the D range pressure oil passage 4102 and the R range pressure oil passage 4104 is discharged. When the spool of the manual valve 4100 is in the D position, the first line pressure oil passage 4010 and the D range pressure oil passage 4102 are communicated, and hydraulic pressure is supplied to the D range pressure oil passage 4102. At this time, the R range pressure oil passage 4104 and the drain port 4105 are communicated, and the R range pressure of the R range pressure oil passage 4104 is discharged from the drain port 4105.

  When the spool of the manual valve 4100 is in the R position, the first line pressure oil passage 4010 and the R range pressure oil passage 4104 are communicated, and the oil pressure is supplied to the R range pressure oil passage 4104. At this time, the D range pressure oil passage 4102 and the drain port 4105 are communicated, and the D range pressure in the D range pressure oil passage 4102 is discharged from the drain port 4105.

  When the spool of the manual valve 4100 is in the N position, both the D range pressure oil passage 4102 and the R range pressure oil passage 4104 are connected to the drain port 4105, and the D range pressure and R of the D range pressure oil passage 4102 are communicated. The R range pressure of the range pressure oil passage 4104 is discharged from the drain port 4105.

  The hydraulic pressure supplied to the D range pressure oil passage 4102 is finally supplied to the B1 brake 3610, the B2 brake 3620, the C1 clutch 3640, and the C2 clutch 3650.

  The hydraulic pressure supplied to the R range pressure oil passage 4104 is finally supplied to the B2 brake 3620.

  The solenoid modulator valve 4200 adjusts the line pressure to a constant pressure. The hydraulic pressure (solenoid modulator pressure) adjusted by the solenoid modulator valve 4200 is supplied to the SLT 4300.

  SL (1) 4210 adjusts the hydraulic pressure supplied to the C1 clutch 3640. SL (2) 4220 adjusts the hydraulic pressure supplied to C2 clutch 3650. SL (3) 4230 adjusts the hydraulic pressure supplied to the B1 brake 3610. SL (4) 4240 adjusts the hydraulic pressure supplied to the B3 brake 3630.

  The SLT 4300 adjusts the solenoid modulator pressure in accordance with a control signal from the ECU 8000 based on the accelerator opening detected by the accelerator opening sensor 8007 to generate a throttle pressure. The throttle pressure is supplied to the primary regulator valve 4006 via the SLT oil passage 4302. The throttle pressure is used as a pilot pressure for the primary regulator valve 4006.

  SL (1) 4210, SL (2) 4220, SL (3) 4230, SL (4) 4240, and SLT 4300 are controlled by a control signal transmitted from ECU 8000.

  The B2 control valve 4500 selectively supplies the hydraulic pressure from one of the D range pressure oil passage 4102 and the R range pressure oil passage 4104 to the B2 brake 3620. A D range pressure oil passage 4102 and an R range pressure oil passage 4104 are connected to the B2 control valve 4500. The B2 control valve 4500 is controlled by the hydraulic pressure supplied from the SL solenoid valve (not shown) and the SLU solenoid valve (not shown) and the biasing force of the spring.

  When the SL solenoid valve is off and the SLU solenoid valve is on, the B2 control valve 4500 is in the state on the left side in FIG. In this case, the B2 brake 3620 is supplied with the hydraulic pressure adjusted from the D range pressure using the hydraulic pressure supplied from the SLU solenoid valve as a pilot pressure.

  When the SL solenoid valve is on and the SLU solenoid valve is off, the B2 control valve 4500 is in the state on the right side in FIG. In this case, the R range pressure is supplied to the B2 brake 3620.

  In the valve body 4000, a compensation oil passage 4610, an oil reservoir chamber 4710, and a switching valve 4810 are further provided. The compensation oil path 4610 has one end connected to the line pressure oil path 4010 and the other end connected to the oil reservoir chamber 4710.

  The oil reservoir chamber 4710 stores ATF (hydraulic pressure). The switching valve 4810 switches between a state where the compensation oil passage 4610 and the oil reservoir chamber 4710 are communicated with each other and a state where the oil reservoir chamber 4710 is blocked according to the temperature of the ATF.

  For example, when the temperature of the ATF is equal to or higher than a predetermined first threshold value, switching valve 4810 communicates compensation oil path 4610 and oil reservoir chamber 4710. When the ATF temperature is lower than the first threshold value and is equal to or higher than a predetermined second threshold value (second threshold value <first threshold value), the switching valve 4810 causes the compensation oil path 4610 and the oil The reservoir chamber 4710 is shut off. Further, when the temperature of the ATF is lower than the second threshold value, the switching valve 4810 communicates the compensation oil passage 4610 and the oil reservoir chamber 4710 again.

  The operation method of the switching valve 4810 is not limited to this. When the ATF temperature is equal to or higher than a predetermined third threshold value, the compensation oil path 4610 and the oil reservoir chamber 4710 are communicated by the switching valve 4810, and shut off when the ATF temperature is lower than the third threshold value. You may make it like this.

  The switching valve 4810 may be operated according to parameters other than the ATF temperature. The switching valve 4810 may be a solenoid valve controlled by the ECU 8000, or may be operated by a shape memory spring. Further, the switching valve 4810 may be operated using a hydraulic pressure output from a solenoid valve controlled by the ECU 8000 as a pilot pressure.

  The operation of the hydraulic control apparatus according to the present embodiment based on the structure as described above will be described.

  For example, when the ATF flow rate in the line pressure oil passage 4010 is sufficient, such as when the temperature of the ATF is equal to or higher than the first threshold value, the compensation oil passage 4610 and the oil reservoir chamber 4710 communicate with each other through the switching valve 4810. Is done. When the ATF temperature is lower than the first threshold value and equal to or higher than a predetermined second threshold value, the compensation oil passage 4610 and the oil reservoir chamber 4710 are shut off by the switching valve 4810. As a result, ATF can be stored in the oil reservoir chamber 4710.

  When the temperature of the ATF is lower than the second threshold value, the compensation oil passage 4610 and the oil reservoir chamber 4710 are communicated again by the switching valve 4810.

  As a result, when the ATF flow rate in the line pressure oil passage 4010 is insufficient, such as in a low temperature state where the volume of the ATF is reduced, the ATF stored in the oil reservoir chamber 4710 can be supplied to the compensation oil passage 4610. Since hydraulic oil is supplied from an oil reservoir chamber 4710 provided separately from the line pressure oil passage 4010, an insufficient ATF flow rate can be compensated for without reducing the line pressure.

<Second Embodiment>
A second embodiment of the present invention will be described with reference to FIG. This embodiment is different from the first embodiment described above in that a compensation oil passage 4620 for connecting the line pressure oil passage 4010 and the secondary pressure oil passage 4012 is provided. Other structures are the same as those in the first embodiment. Their functions are the same. Therefore, those descriptions are not repeated here.

  As shown in FIG. 5, a compensation oil passage 4620, an oil reservoir chamber 4720, and a switching valve 4820 are provided in the valve body 4000. The compensation oil passage 4620 is provided so as to connect the line pressure oil passage 4010 and the secondary pressure oil passage 4012.

  An orifice 4622 and a check valve 4624 are provided on the compensation oil passage 4620. The check valve 4624 allows the ATF to flow from the line pressure oil passage 4010 side to the secondary pressure oil passage 4012 side. On the other hand, the check valve 4624 suppresses the ATF flow from the secondary pressure oil passage 4012 side to the line pressure oil passage 4010 side.

  In the present embodiment, switching valve 4820 switches between a state in which compensation oil passage 4620 and oil reservoir chamber 4720 are in communication with each other and a state in which the oil reservoir chamber 4720 is cut off, depending on the temperature of ATF.

  For example, as in the first embodiment, when the ATF temperature is equal to or higher than a predetermined first threshold value or smaller than the second threshold value, the switching valve 4820 includes the compensation oil path 4620 and the oil. The reservoir chamber 4720 is communicated. When the ATF temperature is lower than the first threshold value and equal to or higher than the second threshold value, switching valve 4820 blocks compensation oil path 4620 and oil reservoir chamber 4720. Note that the operation method of the switching valve 4820 is not limited to this.

  Even with such a configuration, the same effects as those of the first embodiment can be obtained.

<Third Embodiment>
A third embodiment of the present invention will be described with reference to FIG. In the present embodiment, the ATF drained or leaked from the SL (1) 4210 to SL (4) 4240 and the B2 control valve 4500 is returned to the secondary pressure oil passage 4012. It differs from the form. Other structures are the same as those in the first embodiment. Their functions are the same. Therefore, those descriptions are not repeated here.

  As shown in FIG. 6, a concentrated drain oil passage 4630, an exhaust valve 4632, an oil reservoir chamber 4730, and a switching valve 4830 are provided in the valve body 4000.

  Concentrated drain oil passage 4630 is connected to SL (1) 4210 to SL (4) 4240 and the drain port of B2 control valve 4500. Concentrated drain oil passage 4630 is connected to an exhaust valve 4632.

  The ATF drained or leaked from the SL (1) 4210 to SL (4) 4240 and the B2 control valve 4500 is collected in the concentrated drain oil passage 4630. The ATF drained or leaked from the SL (1) 4210 to SL (4) 4240 and the B2 control valve 4500 is returned to the oil pan 4002 through the concentrated drain oil passage 4630 and the exhaust valve 4632.

  It should be noted that leakage or drainage may occur from a device that operates when the hydraulic pressure adjusted by the secondary regulator valve 4008 is supplied (for example, a lockup clutch and a lockup control valve that switches a hydraulic pressure path to be supplied to the lockup clutch). The ATF may be collected in the concentrated drain oil passage 4630.

  Concentrated drain oil passage 4630 is connected to secondary pressure oil passage 4012. A check valve 4634 is provided on the concentrated drain oil passage 4630. The check valve 4634 allows the ATF to flow from the concentrated drain oil passage 4630 side to the secondary pressure oil passage 4012 side. On the other hand, the check valve 4634 suppresses the ATF flow from the secondary pressure oil passage 4012 side to the concentrated drain oil passage 4630 side.

  In the present embodiment, switching valve 4830 switches between a state in which concentrated drain oil passage 4630 and oil reservoir chamber 4730 are in communication with each other and a state in which they are shut off, depending on the temperature of ATF.

  For example, as in the first embodiment, when the ATF temperature is equal to or higher than a predetermined first threshold value or lower than the second threshold value, the switching valve 4830 is connected to the concentrated drain oil passage 4630 and the oil. The reservoir chamber 4730 is communicated. When the ATF temperature is lower than the first threshold value and equal to or higher than the second threshold value, the switching valve 4830 blocks the concentrated drain oil passage 4630 and the oil reservoir chamber 4730 from each other. Note that the operation method of the switching valve 4830 is not limited to this.

  According to this configuration, the same effects as those of the first embodiment described above can be obtained, and drainage or leakage has occurred from the SL (1) 4210 to SL (4) 4240 and the B2 control valve 4500. ATF can be supplied to the secondary regulator valve 4008 without going through the oil pump 4004 or the primary regulator valve 4006. Therefore, even when the ATF supplied from the primary regulator valve 4006 to the secondary regulator valve 4008 is insufficient, a sufficient amount of ATF is supplied to the secondary regulator valve 4008 without increasing the discharge amount from the oil pump 4004. be able to. Therefore, the oil pump 4004 can be downsized or the idling speed can be reduced while suppressing the shortage of the ATF flow rate in the secondary regulator valve 4008.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a schematic block diagram which shows the power train of a vehicle. It is a skeleton figure which shows the gear train in a transmission. It is a figure which shows the operation | movement table | surface of a transmission. It is a figure which shows a part of hydraulic circuit formed in the valve body in the 1st Embodiment of this invention. It is a figure which shows a part of hydraulic circuit formed in the valve body in the 2nd Embodiment of this invention. It is a figure which shows a part of hydraulic circuit formed in the valve body in the 3rd Embodiment of this invention.

Explanation of symbols

  1000 engine, 2000 transmission, 3000 planetary gear unit, 3200 torque converter, 3610 B1 brake, 3620 B2 brake, 3630 B3 brake, 3640 C1 clutch, 3650 C2 clutch, 3660 one-way clutch F, 4000 valve body, 4002 oil pan, 4004 oil pump , 4006 Primary regulator valve, 4008 Secondary regulator valve, 4010 Line pressure oil passage, 4012 Secondary pressure oil passage, 4210 SL1 linear solenoid, 4220 SL2 linear solenoid, 4230 SL3 linear solenoid, 4240 SL4 linear solenoid, 4500 B2 control valve, 4610, 4620 Compensation oil passage, 4622 Orient Scan, 4624,4634 check valve 4630 centralized drain oil passage, 4632 exhaust valve, 4710,4720,4730 oil reservoir chamber, 4810,4820,4830 switching valve.

Claims (5)

A hydraulic control device for an automatic transmission that operates by pressure of hydraulic oil,
A first reservoir for storing hydraulic oil;
A first oil passage through which hydraulic oil stored in the first storage section is supplied by a supply mechanism;
A first control mechanism for controlling the pressure of the hydraulic oil in the first oil passage;
A second oil passage to which hydraulic oil flowing out from the first control mechanism is supplied;
A second control mechanism for controlling the pressure of the hydraulic oil in the second oil passage;
A third oil passage connected to at least one of the first oil passage and the second oil passage;
A second storage unit connected to the third oil passage and storing hydraulic oil;
A switching mechanism that switches between a state in which the third oil passage and the second storage unit are in communication with each other, and a state in which the second storage unit is shut off.
When the temperature of the hydraulic oil exceeds a first threshold value or when the temperature of the hydraulic oil is lower than a second threshold value that is lower than the first threshold value, the switching mechanism includes the third oil passage and When the temperature of the hydraulic oil is lower than the first threshold and equal to or higher than the second threshold, the third oil passage and the second storage are switched to the state where the second storage is in communication. Hydraulic control device for automatic transmission that switches to a state where the parts are shut off . The hydraulic control device for an automatic transmission according to claim 1 , wherein the third oil passage is connected to the first oil passage. The third oil passage includes the first oil passage and the first oil passage so as to supply the hydraulic oil in the first oil passage to the second oil passage, bypassing the first control mechanism. The hydraulic control device for an automatic transmission according to claim 1 , wherein the hydraulic control device is connected to two oil passages. An operating mechanism that operates when hydraulic oil whose pressure is controlled by at least one of the first control mechanism and the second control mechanism is supplied;
The third oil passage supplies the second oil passage with at least one of hydraulic oil discharged from the operation mechanism and hydraulic oil leaked from the operation mechanism. The hydraulic control device for an automatic transmission according to claim 1 , wherein the hydraulic control device is connected to two oil passages. The said 2nd storage part is provided in the valve body in which a said 1st oil path, a said 2nd oil path, and a said 3rd oil path are formed, In any one of Claims 1-4 . Hydraulic control device for automatic transmission.

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