WO2013105233A1 - 油圧制御装置及び車両制御装置 - Google Patents
油圧制御装置及び車両制御装置 Download PDFInfo
- Publication number
- WO2013105233A1 WO2013105233A1 PCT/JP2012/050396 JP2012050396W WO2013105233A1 WO 2013105233 A1 WO2013105233 A1 WO 2013105233A1 JP 2012050396 W JP2012050396 W JP 2012050396W WO 2013105233 A1 WO2013105233 A1 WO 2013105233A1
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- Prior art keywords
- oil
- pressure
- accumulator
- clutch
- hydraulic
- Prior art date
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Classifications
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/02—Conjoint control of vehicle sub-units of different type or different function including control of driveline clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2400/00—Special features of vehicle units
- B60Y2400/70—Gearings
- B60Y2400/72—Continous variable transmissions [CVT]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/0021—Generation or control of line pressure
- F16H2061/0034—Accumulators for fluid pressure supply; Control thereof
Definitions
- the present invention relates to a hydraulic control device and a vehicle control device.
- Patent Document 1 discloses a first accumulator for supplying hydraulic pressure to a clutch drive system when the engine is restarted when returning from idling stop control, and a second accumulator for reducing clutch engagement shock. The structure provided with these is disclosed.
- the configuration including two accumulators for supplying hydraulic pressure at the time of engine restart and reducing the engagement shock increases the number of parts and makes the configuration complicated.
- the present invention has been made in view of the above, and provides a hydraulic control device and vehicle control that can simultaneously realize hydraulic pressure supply to a clutch at the time of engine restart and clutch engagement shock reduction with a simple configuration.
- An object is to provide an apparatus.
- a hydraulic control apparatus includes a mechanical pump that discharges oil by driving a vehicle engine, a hydraulic path that supplies oil discharged by the mechanical pump to a clutch, and the hydraulic pressure
- a clutch pressure control valve for controlling a clutch pressure, which is a hydraulic pressure to be supplied to the clutch, provided on the path; and a clutch provided downstream of the clutch pressure control valve in the hydraulic path and supplying the oil from the hydraulic path
- An accumulator that accumulates oil supplied by the mechanical pump, discharges the accumulated oil, and supplies the accumulated oil to the clutch, upstream of the clutch pressure control valve A first oil path connected to the hydraulic path at a second position and a second oil path connected to the hydraulic path downstream from the selection valve.
- connection control means for controlling connection between the accumulator and the hydraulic path so as to communicate the accumulator with one of the first oil path and the second oil path, and oil supplied by the mechanical pump And a third oil passage supplied to the back pressure side of the accumulator.
- connection control unit communicates the accumulator with the hydraulic path via the first oil path when the engine is stopped, and via the second oil path when the engine is operating. It is preferable to include a switching valve that switches the accumulator so as to communicate with the hydraulic path, and a pressure accumulation control valve that is disposed between the switching valve and the accumulator and controls pressure accumulation and discharge of the accumulator.
- the hydraulic control device includes a check valve that prevents a backflow of oil upstream of the hydraulic path upstream of a connection position with the first oil path on the hydraulic path.
- the third oil passage is connected to the hydraulic passage upstream of the check valve.
- a vehicle control device includes an engine, a clutch, and the hydraulic control device that controls the hydraulic pressure of oil supplied to operate the clutch.
- the eco-run control for stopping the engine during traveling can be executed.
- a single accumulator is connected to the clutch at the time of engine restart depending on whether the accumulator is connected to the hydraulic path through either the first oil path or the second oil path. It can be used as both a function for supplying hydraulic pressure (accumulation / discharge function) and a function for reducing clutch engagement shock (damper function). Furthermore, by supplying the oil supplied by the mechanical pump to the negative pressure side of the accumulator through the third oil passage, the discharge capacity of the accumulator is temporarily reduced and the performance of the accumulator is reduced to the performance required as a damper function. it can. As a result, the hydraulic control device and the vehicle control device according to the present invention have an effect that the hydraulic pressure supply to the clutch when the engine is restarted and the clutch engagement shock can be reduced with a simple configuration.
- FIG. 1 is a schematic diagram showing the configuration of a vehicle equipped with a hydraulic control device according to an embodiment of the present invention.
- FIG. 2 is a diagram showing a schematic configuration of the hydraulic control apparatus in FIG.
- FIG. 3 is a schematic diagram for explaining the discharge operation of the accumulator in FIG.
- FIG. 4 is a schematic diagram for explaining the damper operation of the accumulator in FIG.
- FIG. 5 is a time chart showing the time transition of the clutch pressure Pc1 when the accumulator is used as a damper function.
- FIG. 6 is a flowchart showing the accumulator pressure accumulation process performed by the hydraulic control apparatus of the present embodiment.
- FIG. 7 is a flowchart showing the discharge process of the accumulator performed by the hydraulic control device of the present embodiment.
- FIG. 1 is a schematic diagram showing the configuration of a vehicle equipped with a hydraulic control device according to an embodiment of the present invention.
- FIG. 2 is a diagram showing a schematic configuration of the hydraulic control apparatus in FIG.
- FIG. 8 is a flowchart showing a process of using the accumulator as a damper, which is performed by the hydraulic control device of the present embodiment.
- FIG. 9 is a schematic diagram illustrating a configuration of a hydraulic control device according to a modification of the embodiment of the present invention.
- the vehicle 2 includes an engine 3 as a power source during driving, a drive wheel 4, a power transmission device 5, a hydraulic control device 1, and an ECU (Electronic Control Unit). 7.
- the engine 3 is a driving source (prime mover) for driving the vehicle 2, and generates power that consumes fuel and acts on the driving wheels 4 of the vehicle 2.
- the engine 3 can generate mechanical power (engine torque) on the crankshaft 8 that is an engine output shaft as the fuel burns, and can output this mechanical power from the crankshaft 8 toward the drive wheels 4. .
- the power transmission device 5 transmits power from the engine 3 to the drive wheels 4.
- the power transmission device 5 is provided in a power transmission path from the engine 3 to the drive wheel 4 and is operated by the pressure (hydraulic pressure) of oil as a liquid medium.
- the power transmission device 5 includes a torque converter 9, a forward / reverse switching mechanism 10, a continuously variable transmission mechanism 11, a speed reduction mechanism 12, a differential gear 13, and the like.
- the crankshaft 8 of the engine 3 and the input shaft 14 of the continuously variable transmission mechanism 11 are connected via a torque converter 9, a forward / reverse switching mechanism 10, and the like, and an output shaft 15 of the continuously variable transmission mechanism 11 is connected. It is connected to the drive wheel 4 via the speed reduction mechanism 12, the differential gear 13, the drive shaft 16, and the like.
- the torque converter 9 is disposed between the engine 3 and the forward / reverse switching mechanism 10, and amplifies (or maintains) the power torque transmitted from the engine 3 and transmits it to the forward / reverse switching mechanism 10. It can.
- the torque converter 9 includes a pump impeller 9a and a turbine runner 9b that are rotatably arranged to face each other, and the pump impeller 9a is coupled to the crankshaft 8 through a front cover 9c so as to be integrally rotatable, and the turbine runner 9b is switched forward and backward. It is configured to be connected to the mechanism 10. As the pump impeller 9a and the turbine runner 9b rotate, a viscous fluid such as hydraulic fluid interposed between the pump impeller 9a and the turbine runner 9b circulates and flows. It is possible to amplify and transmit torque while allowing
- the torque converter 9 further includes a lock-up clutch 9d that is provided between the turbine runner 9b and the front cover 9c and is coupled to the turbine runner 9b so as to be integrally rotatable.
- the lock-up clutch 9d is operated by oil pressure supplied from a hydraulic control device 1 described later, and is switched between an engaged state (lock-up ON) and a released state (lock-up OFF) with the front cover 9c.
- the torque converter 9 transmits the torque transmitted from the engine 3 to the forward / reverse switching mechanism 10 as it is.
- the forward / reverse switching mechanism 10 can shift the power (rotational output) from the engine 3 and can switch the rotation direction.
- the forward / reverse switching mechanism 10 includes a planetary gear mechanism 17, a forward / reverse switching clutch (forward clutch) C1 as a friction engagement element, a forward / reverse switching brake (reverse brake) B1, and the like.
- the planetary gear mechanism 17 is a differential mechanism that includes a sun gear, a ring gear, a carrier, and the like as a plurality of rotational elements that can rotate differentially with each other.
- the forward / reverse switching clutch C1 and the forward / reverse switching brake B1 It is an engagement element for switching the operating state of the gear mechanism 17 and can be constituted by, for example, a frictional engagement mechanism such as a multi-plate clutch.
- a hydraulic wet multi-plate clutch is used.
- the forward / reverse switching clutch C1 and the forward / reverse switching brake B1 are operated by the pressure of oil supplied from the hydraulic control device 1 described later, and the operating state is switched.
- the forward / reverse switching clutch C1 is in the engaged state (ON state) and the forward / reverse switching brake B1 is in the released state (OFF state)
- the forward / reverse switching mechanism 10 rotates the power from the engine 3 in the normal rotation (vehicle 2). Is transmitted to the input shaft 14 in the direction in which the input shaft 14 rotates as the vehicle advances.
- the forward / reverse switching mechanism 10 rotates the power from the engine 3 in reverse rotation (when the vehicle 2 moves backward, the input shaft 14 In the direction of rotation).
- the forward / reverse switching mechanism 10 is in a released state for both the forward / reverse switching clutch C1 and the forward / reverse switching brake B1.
- the forward / reverse switching clutch C1 and the forward / reverse switching brake B1 are collectively referred to as “C1 clutch”, and a control system for controlling engagement / release of the C1 clutch is collectively referred to as “C1 control”. Called “system 18”. Further, the C1 clutch and the C1 control system 18 are collectively expressed simply as “clutch”.
- the continuously variable transmission mechanism 11 is a transmission that is provided between the forward / reverse switching mechanism 10 and the drive wheel 4 in the power transmission path from the engine 3 to the drive wheel 4 and that can output the power of the engine 3 by shifting the power. is there.
- the continuously variable transmission mechanism 11 is operated by the pressure of oil supplied from a hydraulic control device 1 described later.
- the continuously variable transmission mechanism 11 is, for example, a known belt-type continuously variable automatic transmission (CVT).
- the continuously variable transmission mechanism 11 includes a primary pulley 20 provided on the engine 3 side, a secondary pulley 21 provided on the drive wheel 4 side, and a belt 22.
- the primary pulley 20 is connected to the input shaft 14.
- the secondary pulley 21 is connected to the output shaft 15.
- the belt 22 is stretched between the primary pulley 20 and the secondary pulley 21.
- the continuously variable transmission mechanism 11 operates the primary pulley side actuator and the secondary pulley side actuator by the pressure of oil supplied from a hydraulic control device 1 described later, and changes the gear ratio steplessly by changing the pulley ratio. Can do. Similarly, the belt clamping pressure can be controlled.
- the reduction mechanism 12 reduces the rotational speed of the power from the continuously variable transmission mechanism 11 and transmits it to the differential gear 13.
- the differential gear 13 transmits the power from the speed reduction mechanism 12 to each drive wheel 4 via each drive shaft 16.
- the differential gear 13 absorbs the difference in rotational speed between the center side of the turning, that is, the inner driving wheel 4 and the outer driving wheel 4 that occurs when the vehicle 2 turns.
- the power transmission device 5 configured as described above drives the power generated by the engine 3 via a torque converter 9, a forward / reverse switching mechanism 10, a continuously variable transmission mechanism 11, a speed reduction mechanism 12, a differential gear 13, and the like. 4 can be transmitted. As a result, the driving force [N] is generated on the contact surface of the driving wheel 4 with the road surface, and the vehicle 2 can travel by this.
- the hydraulic control device 1 uses a hydraulic pressure of oil as a fluid to lock up the clutch 9d of the torque converter 9, the forward / reverse switching clutch C1 and the forward / reverse switching brake B1 of the forward / reverse switching mechanism 10, the primary pulley 20 of the continuously variable transmission mechanism 11, and
- the power transmission device 5 including the secondary pulley 21 and the like is operated.
- the hydraulic control device 1 includes, for example, various hydraulic control circuits that are controlled by the ECU 7.
- the hydraulic control device 1 is configured to include a plurality of oil passages, an oil reservoir, an oil pump, a plurality of electromagnetic valves, and the like, and according to a signal from the ECU 7 described later, Control the flow rate or hydraulic pressure.
- the hydraulic control device 1 also functions as a lubricating oil supply device that lubricates predetermined portions of the power transmission device 5. The details of the configuration of the hydraulic control device 1 will be described later with reference to FIG.
- the ECU 7 controls driving of each part of the vehicle 2.
- the ECU 7 is physically an electronic circuit mainly composed of a known microcomputer including a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), and an interface.
- the function of the ECU 7 is to load an application program held in the ROM into the RAM and execute it by the CPU, thereby operating various devices in the vehicle 2 under the control of the CPU and reading out data from the RAM or ROM. And writing.
- the ECU 7 controls each part of the power transmission device 5 such as the torque converter 9, the forward / reverse switching mechanism 10, and the continuously variable transmission mechanism 11 by controlling the hydraulic control device 1 described above.
- the ECU 7 is not limited to the above functions, but also includes various other functions used for various controls of the vehicle 2.
- the ECU 7 includes an engine ECU that controls the engine 3, a T / M ECU that controls the power transmission device 5 (hydraulic control device 1), and an idling stop (S & S (start and stop)) control.
- the configuration may include a plurality of ECUs such as S & S ECUs.
- the ECU 7 is connected to various sensors in the vehicle 2 (not shown in FIG. 1) and receives detection signals from the various sensors, and controls the driving of each part of the vehicle 2 based on these detection signals. can do.
- the vehicle 2 according to the present embodiment has a function of stopping the engine 3 while the vehicle 2 is stopped or traveling, so-called idling stop control (in this embodiment, “S & S control” and “eco-run control”) in order to improve fuel efficiency.
- the ECU 7 is configured to be able to execute idling stop control when predetermined conditions are satisfied based on various sensor information.
- FIG. 2 is a diagram showing a schematic configuration of the hydraulic control device 1 in FIG.
- the hydraulic control device 1 includes a mechanical mechanical pump (mechanical pump) 31 that is driven by driving of the engine 3 as an oil supply source that supplies oil to each part of the power transmission device 5. .
- the mechanical pump 31 sucks, compresses and discharges the oil stored in the drain 32 in the hydraulic control device 1.
- the mechanical pump 31 can supply the discharged oil to the power transmission device 5 via the hydraulic path 33.
- a primary regulator valve 34 is provided in the hydraulic path 33.
- the primary regulator valve 34 regulates the hydraulic pressure generated by the mechanical pump 31.
- the primary regulator valve 34 is supplied with a control pressure by an SLS linear solenoid 35, and the primary regulator valve 34 adjusts the hydraulic pressure in the hydraulic path 33 in accordance with the control pressure. Then, the hydraulic pressure in the hydraulic path 33 regulated by the primary regulator valve 34 is used as the line pressure PL.
- the primary regulator valve 34 for example, a spool valve in which a valve body (spool) slides in the axial direction in the valve body to open / close or switch a flow path can be applied, and a hydraulic path 33 is connected to an input port.
- the SLS linear solenoid 35 is connected to the pilot port for inputting the pilot pressure, the control pressure is inputted, and the excess flow generated by the regulation of the line pressure PL can be discharged from the output port.
- An L / U control system 36 that controls engagement / release of the lock-up clutch 9d of the torque converter 9 is connected to the output port of the primary regulator valve 34, and when an excess flow is generated from the primary regulator valve 34, This surplus flow is configured to be supplied to the L / U control system 36 (or a low-pressure control system that can be controlled at a lower pressure than the continuously variable transmission mechanism 11). Further, the surplus flow from the primary regulator valve 34 is configured to be supplied to each part lubrication at a predetermined location in the power transmission device 5. Although not shown in FIG. 2, an oil passage is formed so that the surplus flow supplied to the L / U control system 36 and each part lubrication is finally returned to the drain 32.
- the mechanical pump 31 is connected to the C1 control system 18 (the forward / reverse switching clutch C1 and the forward / reverse switching brake B1) of the forward / reverse switching mechanism 10 and the continuously variable transmission mechanism 11 via the hydraulic path 33 by the primary regulator valve 34.
- the hydraulic pressure adjusted to the line pressure PL is connected so that supply is possible.
- the LPM No. 1 is placed on the clutch oil path 38 connected to the C1 control system 18.
- Two valves 37 are provided. LPM No. Similar to the primary regulator valve 34, the two valve 37 is a spool valve, for example, and outputs a predetermined hydraulic pressure Plpm2 that is regulated (depressurized) using the line pressure PL introduced into the valve as a source pressure.
- the clutch oil passage 38 is an LPM No.
- a lubricating oil passage 39 for supplying oil of the oil pressure Plpm2 to lubricate each part at a predetermined location in the power transmission device 5 is connected.
- An SLC linear solenoid 40 (clutch pressure control valve) is provided on the clutch oil passage 38 downstream from the branch with the lubricating oil passage 39. Similar to the SLS linear solenoid 35 and the like, the SLC linear solenoid 40 is an electromagnetic valve that generates a control pressure in accordance with a current value determined by a duty signal (duty value) transmitted from the ECU 7. In the present embodiment, the SLC linear solenoid 40 controls the control pressure (clutch pressure) Pc1 supplied to the C1 control system 18 using the hydraulic pressure Plpm2 as a source pressure.
- a manual valve 41 (selection valve) is provided on the downstream side of the SLC linear solenoid 40 in the clutch oil passage 38.
- the manual valve 41 selects a clutch that supplies oil from the hydraulic path 33.
- the manual valve 41 is linked with the shift operation of the driver of the vehicle 2 between the clutch oil path 38 and the C1 control system 18. The connection relationship is switched.
- the manual valve 41 can switch communication / disconnection between the clutch oil passage 38 and the forward / reverse switching clutch C1 and the forward / reverse switching brake B1.
- the shift position is “D (forward)”
- the manual valve 41 can control the forward / reverse switching clutch C1 by connecting the clutch oil passage 38 to the forward / reverse switching clutch C1 in the C1 control system 18.
- the manual valve 41 is configured to connect the forward / reverse switching brake B1 of the C1 control system 18 to the discharge port Ex, and to let the oil acting on the forward / reverse switching brake B1 escape from the discharge port Ex.
- the manual valve 41 can control the forward / reverse switching brake B1 by connecting the clutch oil passage 38 to the forward / reverse switching brake B1 in the C1 control system 18. And at this time, the manual valve 41 is configured to connect the forward / reverse switching clutch C1 of the C1 control system 18 to the discharge port Ex, and to let the oil acting on the forward / reverse switching clutch C1 escape from the discharge port Ex. Further, when the shift position is “N (neutral)”, the manual valve 41 disconnects both the forward / reverse switching clutch C1 and the forward / reverse switching brake B1 from the clutch oil passage 38 and connects it to the discharge port Ex. . As a result, the oil acting on the forward / reverse switching clutch C1 and the forward / reverse switching brake B1 is discharged from the discharge port Ex.
- the accumulator 44 is connected on the oil passage 38 for clutches.
- the accumulator 44 is configured to store and hold (accumulate) the hydraulic pressure supplied from the mechanical pump 31 when the mechanical pump 31 is driven, and to supply the held hydraulic pressure to the C1 control system 18 as necessary. ing.
- FIG. 3 is a schematic diagram for explaining the discharge operation of the accumulator 44
- FIG. 4 is a schematic diagram for explaining the damper operation of the accumulator 44
- FIG. 5 is a diagram when the accumulator 44 is used as a damper. It is a time chart which shows the time transition of the clutch pressure Pc1.
- the accumulator 44 includes a stepped piston 44b fitted in a stepped cylinder 44a so as to be slidable in one direction. Due to the small diameter portion of the stepped piston 44b, a pressure accumulation chamber 44c for accumulating oil is formed at the small diameter side end portion in the stepped cylinder 44a, and the volume of the pressure accumulation chamber 44c can be changed by the movement of the stepped piston 44b. It is configured.
- the accumulator 44 has a pressure accumulating chamber 44c connected to a connecting oil passage 42 for communicating the accumulator 44 and the hydraulic passage 33. Through this connecting oil passage 42, oil is introduced into the pressure accumulating chamber 44c during pressure accumulation. During discharge, oil is discharged from the pressure accumulating chamber 44c.
- a first back pressure chamber 44d is formed by the large diameter portion of the stepped piston 44b at the large diameter side end portion in the stepped cylinder 44a of the accumulator 44.
- the first back pressure chamber 44d is provided with a spring 44f for urging the stepped piston 44b toward the pressure accumulating chamber 44c, and the urging force is changed according to the deformation of the spring 44f due to the sliding of the stepped piston 44b. In other words, the back pressure can be changed.
- the stepped piston 44b is pushed in to expand the volume of the accumulator 44c and the oil is stored inside. This back pressure and the pressure of the oil accumulated in the accumulator 44c (accumulator pressure Pacc. ) Is balanced.
- the accumulator 44 is discharged, the accumulated oil is discharged from the inside by pushing out the piston using the biasing force of the spring 44 f and supplied to the C1 control system 18.
- the back pressure that can be generated by the spring 44f has a maximum value when the large-diameter side end surface of the stepped piston 44b abuts against the large-diameter side end of the stepped cylinder 44a.
- the maximum value of the back pressure is adjusted, for example, by adjusting the spring length or spring constant of the spring 44f so that the clutch pressure Pc1 can be maintained at least at the packed pressure when oil is discharged from the accumulator 44. This can be set in advance.
- pack packing pressure refers to a hydraulic pressure that can fill the clutch pack (the hydraulic oil chamber of the C1 clutch) with hydraulic oil so that the clutch plate of the C1 clutch comes into contact with (clogs) the friction material. .
- a second back pressure chamber 44e is formed between the stepped portion of the stepped cylinder 44a of the accumulator 44 and the stepped portion of the stepped piston 44b.
- the accumulator 44 is configured to be able to adjust the back pressure of the stepped piston 44b by adjusting the amount of oil supplied to the second back pressure chamber 44e. As the amount of oil supplied to the second back pressure chamber 44e increases, the balance position of the stepped piston 44b moves toward the large diameter end of the stepped cylinder 44a, and the oil discharge capacity from the pressure accumulating chamber 44c decreases. Can be made.
- the second back pressure chamber 44e is connected to the back pressure control oil passage 50 (third oil passage), and oil is introduced / discharged through the back pressure control oil passage 50.
- Accumulation and discharge of the accumulator 44 are controlled by a pressure accumulation control valve 43 provided on the connection oil passage 42.
- the pressure accumulation control valve 43 is, for example, an electromagnetic poppet valve, and can be opened and closed by adjusting a supply current by the ECU 7.
- the pressure accumulation control valve 43 can be a normally closed valve that is opened when current is supplied and normally closed when current is not supplied.
- the pressure accumulation control valve 43 may use another valve structure such as a spool valve.
- a pressure sensor 45 for detecting the pressure (accumulator pressure) Pacc of the oil accumulated in the accumulator 44 is provided, and information on the detected accumulator pressure Pacc is transmitted to the ECU 7. It is configured.
- the accumulator 44 and the pressure accumulation control valve 43 are connected to the two oil passages of the first oil passage 46 and the second oil passage 47 via the connection oil passage 42, and the first oil passage 46 and The second oil passage 47 is connected to the hydraulic passage 33 (the clutch oil passage 38) so as to communicate therewith.
- the position where the first oil passage 46 is connected to the hydraulic passage 33 is on the upstream side of the SLC linear solenoid 40, preferably LPM No. More preferably, it is downstream of the two valves 37, more preferably downstream of the branch of the oil passage 38 for the clutch of the hydraulic passage 33 with the lubricating oil passage 39.
- the position where the second oil passage 47 is connected to the hydraulic passage 33 is downstream of the manual valve 41.
- the second oil passage 47 is connected at a position on the hydraulic path 33 where the hydraulic pressure is the same level as the hydraulic pressure actually supplied to the C1 clutch and the C1 control system 18.
- the end of the first oil passage 46 and the second oil passage 47 opposite to the side connected to the hydraulic passage 33 is connected to the switching valve 48.
- the switching valve 48 is also connected to the accumulator 44 via the connection oil passage 42, and selects one of the first oil passage 46 and the second oil passage 47 to select the accumulator 44 and the hydraulic passage 33 (the clutch oil passage 38. ) To communicate with each other.
- the switching valve 48 can switch the oil path to be selected by the line pressure PL generated by driving the engine 3. More specifically, when the mechanical pump 31 is driven when the engine 3 is driven and the line pressure PL is greater than or equal to a predetermined value, the accumulator 44 is connected to the hydraulic path 33 (the clutch oil path via the second oil path 47). 38) so as to be able to communicate with each other (in the configuration illustrated in FIG. 2, the switching valve 48 moves to the left by PL). On the other hand, when the engine 3 is stopped, the driving of the mechanical pump 31 is also stopped, and when the line pressure PL decreases below a predetermined value, the accumulator 44 is connected to the hydraulic path 33 (the clutch oil path 38 via the first oil path 46). 2) (in the configuration illustrated in FIG. 2, the switching valve 48 is moved to the right by the spring).
- such a configuration of the switching valve 48, the first oil passage 46, and the second oil passage 47 allows the vehicle 3 to travel normally, that is, the engine 3 is driven and the mechanical pump 31 discharges the oil having the line pressure PL.
- the switching valve 48 is switched to communicate with the second oil passage 47.
- the accumulator 44 is connected to the hydraulic path 33 on the downstream side of the manual valve 41 via the second oil path 47.
- the pressure accumulation process for accumulating oil in the accumulator 44 can be performed by opening the pressure accumulation control valve 43 as appropriate and then closing the valve.
- the accumulator 44 In a state where the accumulator 44 is accumulating and holding pressure, the accumulator 44 has a stepped piston 44b having a large diameter of the stepped cylinder 44a, as shown in the left side of FIG.
- the pressure accumulation control valve 43 is closed (closed) in a state in which the pressure accumulation chamber 44c reaches the maximum volume while hitting the side end, and the oil of the accumulator pressure Pacc corresponding to the pack packing pressure is held in the pressure accumulation chamber.
- the vehicle 2 is configured to be able to perform the idling stop control as described above.
- the engine 3 It is possible to execute idling stop traveling that travels in a state in which both the stop and release of the C1 clutch are performed. While the idling stop traveling is being executed, the engine 3 is stopped and the mechanical pump does not output the oil having the line pressure PL. Therefore, in the present embodiment, the switching valve 48 is switched to communicate with the first oil passage 46. At this time, the accumulator 44 is connected to the hydraulic path 33 on the upstream side of the SLC linear solenoid 40 via the first oil path 46.
- the pressure accumulation control valve 43 is maintained with the switching valve 48 communicating with the first oil passage 46 as described above. Is opened at an appropriate timing, so that the discharge process for discharging the oil accumulated in the accumulator 44 can be performed.
- the oil accumulated in the accumulator 44 is discharged to the hydraulic path 33 upstream of the SLC linear solenoid 40 via the first oil path 46.
- the original pressure Plpm2 for generating the clutch pressure Pc1 is increased by the SLC linear solenoid 40, so that the clutch pressure Pc1 can be set as the packed pressure by appropriately controlling the SLC linear solenoid 40.
- the stepped piston 44b is moved to the small diameter side of the stepped cylinder 44a by the urging force of the spring 44f.
- the oil that hits the end and is accumulated in the pressure accumulating chamber 44c is discharged through the connecting oil passage 42.
- a check valve 49 (check valve) is provided upstream of the connection position of the first oil path 46 on the clutch oil path 38 (in the example of FIG. 2, the position downstream of the lubrication oil path 39).
- the oil discharged from the accumulator 44 is prevented from leaking or flowing back to the upstream side, so that the hydraulic pressure Plpm2 can be efficiently increased by the accumulator 44. Yes.
- the switching valve 48 and the pressure accumulation control valve 43 connect the accumulator 44 so as to be able to communicate with one of the first oil passage 46 and the second oil passage 47, and connect the accumulator 44 to the hydraulic passage 33 (the clutch oil passage 38). ) Function as “connection control means” for controlling the connection with the device.
- the back pressure control oil passage 50 (third oil passage) connected to the second back pressure chamber 44e of the accumulator 44 is connected to the hydraulic passage 33 (clutch oil passage 38) upstream of the check valve 49. Yes. That is, the back pressure control oil passage 50 is configured to be able to introduce oil of the oil pressure Plpm2 of the clutch oil passage 38 generated during operation of the mechanical pump 31 into the second back pressure chamber 44e of the accumulator 44. .
- the manual valve 41 when a shift operation is performed by the driver while the vehicle is traveling, the manual valve 41 is displaced according to the shift position. Due to the displacement of the manual valve 41, a situation occurs in which the state of communicating / blocking the oil flow in the clutch oil passage 38 is switched. For example, when the shift position is switched from D to N, the forward / reverse switching clutch C1 of the C1 control system 18 is switched from a state communicating with the clutch oil passage 38 to a disconnected state. Further, the oil remaining between the forward / reverse switching clutch C ⁇ b> 1 and the manual valve 41 is discharged from the discharge port Ex of the manual valve 41.
- the accumulator 44 is in communication with the hydraulic path 33 on the downstream side of the manual valve 41 via the second oil path 47, and a predetermined condition (details are shown in FIG. 8).
- the pressure accumulation control valve 43 is configured to be opened when the following condition is satisfied with reference to FIG. Accordingly, the accumulator 44 can be used as a damper function, and the fluctuation of the clutch pressure Pc1 can be reduced by absorbing the fluctuation of the clutch pressure Pc1 due to the displacement of the manual valve 41 by the accumulator 44.
- the pressure of the oil (accumulator pressure) Pacc (initial hydraulic pressure) held in the pressure accumulating chamber 44c can be expressed by the following equation (2).
- As is the area of the end face on the small diameter side (downward in FIGS. 3 and 4).
- Vacc As ⁇ X (3)
- the back pressure Pe is supplied to the second back pressure chamber 44e of the accumulator 44 because the engine 3 and the mechanical pump 31 are being driven.
- the accumulator 44 starts from the state where the stepped piston 44b is balanced at the height h of the pressure accumulating chamber 44c as shown on the right side of FIG. Of the clutch pressure Pc1 flows into the pressure accumulating chamber 44c. Then, as shown on the left side of FIG. 4, after the stepped piston is pushed into a state where the biasing force Fs by the spring 44f, the force Fe by the back pressure Pe, and the force Fc1 by the clutch pressure Pc1 are balanced, the pressure accumulating chamber 44c The oil of the hydraulic pressure Pdumper and the volume Vdumper that has been held inside is discharged. The stepped piston 44b is again balanced at the height h of the pressure accumulating chamber 44c, and the oil discharged from the accumulator 44 is discharged from the discharge port Ex of the manual valve 41.
- the performance of the accumulator 44 is equivalent to that the hydraulic pressure capable of accumulating is Pdumper and the amount of oil that can be discharged (discharge volume) is Vdumper.
- the hydraulic pressure Pdumper and the discharge volume Vdumper when using the damper are smaller than the hydraulic pressure Pacc and the discharge amount Vacc during pressure accumulation discharge.
- the back pressure Pe it is possible to have at least two types of performance with a single accumulator.
- the discharge capacity and hydraulic level are the performance required for the damper. Can be lowered.
- the hydraulic pressure level and the discharge capacity when using the damper function can be controlled.
- FIG. 5 shows the time transition of the clutch pressure Pc1 supplied to the forward / reverse switching clutch C1 when the shift position transitions from D to N.
- the graph A in the figure shows the time transition of the clutch pressure Pc1 when the back pressure Pe is supplied to the accumulator 44, and the graph B shows the time transition of the clutch pressure Pc1 when the back pressure Pe is not supplied to the accumulator 44. Is shown.
- the shift position is D and the forward / reverse switching clutch C1 is in communication with the clutch oil passage 38, and the clutch pressure Pc1 is maintained at a predetermined value.
- the clutch oil passage 38 leading to the forward / reverse switching clutch C1 is blocked from the upstream side of the manual valve 41, and the manual valve discharge port Ex The oil remaining in the clutch oil passage 38 begins to be discharged from the discharge port.
- the accumulator 44 functions as a damper of the discharge capacity Vacc. Therefore, as shown in the graph B, the speed of oil removal from the C1 control system 18 is alleviated and the clutch pressure Pc1 is reduced. The rate is also relatively small.
- the clutch pressure Pc1 decreases below the driving force transmission hydraulic pressure (the hydraulic pressure at which the forward / reverse switching clutch C1 can transmit the driving force), and the forward / reverse switching clutch C1 opens.
- the accumulator 44 functions as a damper of the discharge capacity Vdumper. Since the discharge capacity Vdumper is smaller than Vacc as shown in the above equation (8), in this case, as shown in the graph A, the speed of oil removal from the C1 control system 18 becomes faster than the graph B (when no back pressure is supplied). The rate of decrease of the clutch pressure Pc1 is also larger than that in the graph B (when no back pressure is supplied). For this reason, at time T2 earlier than time T3, the clutch pressure Pc1 decreases below the driving force transmission hydraulic pressure, and the forward / reverse switching clutch C1 is released.
- FIG. 6 is a flowchart showing a pressure accumulation process of the accumulator 44 performed by the hydraulic control device 1 of the present embodiment
- FIG. 7 shows a discharge process of the accumulator 44 performed by the hydraulic control device 1 of the present embodiment
- FIG. 8 is a flowchart showing a process of using the accumulator 44 implemented as a damper by the hydraulic control device 1 of the present embodiment.
- Each process shown in FIGS. 6 to 8 is performed by the ECU 7 using the pressure accumulation control valve 43 of the hydraulic control device 1 and various sensor information of the vehicle 2.
- step S101 it is confirmed whether or not the engine 3 is operating. If the engine 3 is operating, the process proceeds to step S102. If the engine 3 is stopped, the process returns to step S101.
- step S101 If it is determined in step S101 that the engine 3 is operating, it is next checked whether or not the accumulator 44 has already accumulated pressure (S102). When there is no pressure accumulation in the accumulator 44, the process proceeds to step S103. If the accumulator 44 has accumulated pressure, the process returns to step S101.
- the prohibition condition of the pressure accumulation process is, for example, a state in which control for releasing the forward / reverse switching clutch C1 is performed immediately before shifting to the idling stop traveling, or a return / forward switching clutch that returns from the idling stop traveling.
- the case where the clutch pressure Pc1 is controlled by the SLC linear solenoid 40 such as a state in which the control for engaging C1 is performed, can be included, and the case where the responsiveness is required for the control of the C1 control system 18 can be included. Further, it may include a case where the flow rate of the hydraulic path 33 (valve body) is large, such as a state where the engine speed is low, a state where the oil temperature in the hydraulic control device 1 is high, and a state where the speed is high.
- step S103 when the pressure accumulation is prohibited, the pressure accumulation control valve 43 is closed (closed), and the process returns to step S101.
- the pressure accumulation control valve 43 is opened (opened) (S104).
- the switching valve 48 is switched to communicate with the second oil passage 47, and the accumulator 44 is connected to the second oil passage 47. Then, oil is introduced from the clutch oil passage 38 downstream of the manual valve 41.
- the accumulator pressure Pacc is equal to or higher than a predetermined hydraulic pressure (S105). If it is equal to or higher than the predetermined oil pressure, the pressure accumulation control valve 43 is closed (closed) assuming that the accumulator 44 has sufficiently accumulated pressure (S107), and the process is terminated. On the other hand, if the predetermined hydraulic pressure has not been reached, the pressure accumulation control valve 43 is kept open (S106), and the process directly returns to step S105.
- step S201 it is confirmed whether or not S & S control (idling stop control) is being executed. If the S & S control is being performed, the process proceeds to step S202. If S & S control is not executed, the process returns to step S201.
- the engine return request is a command for returning from idling stop running to engine running, and is detected using, for example, a state where the brake is turned off, the negative pressure of the brake is lowered, or the battery voltage is lowered as a trigger. .
- step S202 If there is no engine return request in step S202, the pressure in the accumulator 44 is maintained with the pressure accumulation control valve 43 closed, and the process returns to step S201.
- step S202 if there is an engine return request in step S202, it is necessary to increase the clutch pressure Pc1 to the pack packing pressure before the engagement control of the forward / reverse switching clutch C1 is performed after the engine 3 is restarted.
- the pressure accumulation control valve 43 is opened (opened) (S203), and accordingly, an engine start request is issued to the starter, and restart control of the engine 3 is started.
- the switching valve 48 is switched to communicate with the first oil passage 46. Therefore, the accumulator 44 discharges oil to the clutch oil passage 38 upstream of the SLC linear solenoid 40 via the first oil passage 46.
- the hydraulic pressure Plpm2 that is the original pressure of the clutch pressure Pc1 controlled by the SLC linear solenoid 40 can be increased, and the clutch pressure Pc1 can be increased to generate a pack packing pressure (approximately about 0.1 MPa).
- the pressure accumulation control valve 43 remains open (opened) (S205), and the process returns to step S204.
- the pressure accumulation control valve 43 is closed to improve the control response of the clutch pressure Pc1 by the SLC linear solenoid 40 (S206), and the oil supplied from the mechanical pump 31 is supplied to the hydraulic path 33. From being introduced into the accumulator 44.
- step S301 it is confirmed whether or not the engine 3 is operating. If the engine 3 is operating, the process proceeds to step S302. If the engine 3 is stopped, the process returns to S301.
- step S301 If it is determined in step S301 that the engine is operating, it is confirmed whether or not it is permitted to use the accumulator 44 as a damper function (S302).
- the accumulator 44 it is preferable to use the accumulator 44 as a damper function when, for example, the vehicle 2 is parked or stopped, the shift position changes from D (drive) to R (reverse), N (neutral), P (parking). ) And other situations where an operation to change to another gear position can occur.
- the manual valve 41 is displaced in accordance with the shift operation, so that the clutch pressure Pc1 varies.
- damper function permission condition For example, detecting that the vehicle speed has become 0 or that a shift operation has actually been performed may be set. it can. Then, when the damper function permission condition is satisfied, it can be determined that the use of the accumulator 44 as a damper function is permitted.
- step S302 If it is determined in step S302 that the damper function is not permitted, the process returns to step S301.
- step S302 If it is determined in step S302 that the damper function is permitted, the pressure accumulation control valve 43 is opened (S303). At this time, since the engine 3 is operating and the line pressure PL is generated, the switching valve 48 is switched so as to communicate with the second oil passage 47, and the accumulator 44 is connected via the second oil passage 47. Thus, the clutch fluid passage 38 is in communication with the downstream side of the manual valve 41. In this state, when the shift operation is performed, the manual valve 41 is displaced, and the clutch pressure Pc1, which is the hydraulic pressure supplied to the C1 control system 18, fluctuates, the fluctuation is introduced into the accumulator 44 through the second oil passage 47. Therefore, the fluctuation of the clutch pressure Pc1 is suppressed.
- the clutch pressure Pc1 which is the hydraulic pressure supplied to the C1 control system 18
- the hydraulic control apparatus 1 includes a mechanical pump 31 that discharges oil by driving the engine 3 of the vehicle 2, and a hydraulic path 33 (clutch oil path 38 that supplies oil discharged by the mechanical pump 31 to the C1 control system 18. ), An SLC linear solenoid 40 that controls the clutch pressure Pc1 that is hydraulic pressure supplied to the C1 control system 18 and a downstream of the SLC linear solenoid 40 of the hydraulic path 33. And a manual valve 41 for selecting a clutch (forward / reverse switching clutch C1 or forward / reverse switching brake B1) for supplying oil from the vehicle.
- the hydraulic control device 1 accumulates the oil supplied by the mechanical pump 31, discharges the accumulated oil and supplies it to the C1 control system 18, and a hydraulic path 33 (upstream from the SLC linear solenoid 40 ( A first oil passage 46 connected to the clutch oil passage 38), a second oil passage 47 connected to the hydraulic passage 33 (clutch oil passage 38) on the downstream side of the manual valve 41, and an accumulator 44.
- a connection control means switching valve 48 and pressure accumulation control valve 43 for controlling the connection between the accumulator 44 and the hydraulic pressure path 33 and the mechanical pump 31 so as to communicate with one of the first oil path 46 and the second oil path 47.
- a back pressure control oil passage 50 that supplies oil to the back pressure side of the accumulator 44.
- the accumulator 44 can be connected to the hydraulic path 33 (the clutch oil path 38) via either the first oil path 46 or the second oil path 47.
- the accumulator 44 In a state where the accumulator 44 communicates with the second oil passage 47, the accumulator 44 is connected to the hydraulic passage 33 (clutch oil passage 38) on the upstream side of the SLC linear solenoid 40. If the oil accumulated in the accumulator 44 is discharged in this state, the original pressure Plpm2 of the clutch pressure Pc1 generated by the SLC linear solenoid 40 can be increased, and the clutch pressure Pc1 can be controlled to the packed pressure. It becomes. That is, in this state, the accumulator 44 can be effectively used as a pressure accumulation / discharge function for securing the pack packing pressure supplied to the C1 control system 18 when the engine is restarted when returning from the idling stop control. it can.
- the accumulator 44 in a state where the accumulator 44 communicates with the first oil passage 46, the accumulator 44 is connected to the hydraulic passage 33 (clutch oil passage 38) on the downstream side of the manual valve 41. If the accumulator 44 is communicated with the clutch oil passage 38 in this state, the oil can be introduced from the clutch oil passage 38 to the accumulator 44, so that the fluctuation of the clutch pressure Pc1 due to the displacement of the manual valve 41 can be absorbed.
- the discharge capacity of the accumulator 44 can be temporarily reduced to a level required for the damper function, It is possible to reduce the time for oil to drain from the clutch, which is disconnected from the hydraulic path 33 by the valve 41, to the discharge port Ex. That is, in this state, the accumulator 44 can be effectively used as a damper function for reducing a shock (DN shock) when the C1 control system 18 is engaged due to a shift operation.
- DN shock a shock
- the single accumulator 44 is connected to the C1 control system 18 at the time of engine restart. It can be used as both a function for supplying hydraulic pressure (accumulation / discharge function) and a function for reducing engagement shock of the C1 control system 18 (damper function). As a result, it is not necessary to install a plurality of accumulators in order to realize these plurality of functions, and a plurality of functions can be realized with a simple configuration using only a single accumulator.
- connection control means communicates the accumulator 44 with the hydraulic path 33 (clutch oil path 38) via the first oil path 46 when the engine 3 is stopped, During operation, the accumulator 44 is disposed via the second oil passage 47 so as to communicate with the hydraulic passage 33 (clutch oil passage 38), and is disposed between the switching valve 48 and the accumulator 44. And a pressure accumulation control valve 43 for controlling discharge.
- the switching valve 48 is switched according to the operating state of the engine 3, and the accumulator 44 is in communication with the second oil passage 47 by the switching valve 48 during normal travel when the engine 3 is operated.
- the accumulator 44 is in communication with the first oil passage 46 by the switching valve 48.
- the switching valve 48 can be switched depending on the presence / absence of the line pressure PL, and electrical control is not required. Therefore, it is not necessary to prepare a control system, and the cost can be reduced.
- the hydraulic control device 1 of the present embodiment causes the oil to flow backward to the upstream side of the hydraulic path 33 upstream of the connection position with the first oil path 46 on the hydraulic path 33 (clutch oil path 38).
- a check valve 49 for preventing is provided.
- the back pressure control oil passage 50 is connected to the hydraulic passage 33 (clutch oil passage 38) on the upstream side of the check valve 49.
- the vehicle control apparatus includes an engine 3, a C1 clutch, and the hydraulic control apparatus 1 that controls the hydraulic pressure of oil supplied to operate the C1 clutch.
- the eco-run control (idling stop control) for stopping 3 can be executed.
- the clutch pressure Pc1 supplied to the C1 control system 18 that controls the C1 clutch is performed by performing a discharge process of the accumulator 44 of the hydraulic control device 1. (For example, pack packing pressure) can be controlled, and the clutch control upon return from the eco-run control can be performed smoothly.
- FIG. 9 shows an example of the configuration of the hydraulic control device 1a when AT is applied as the transmission. 9 is located upstream of the connection position of the manual valve 41 with the hydraulic path 33 of the back pressure control oil path 50 (in the hydraulic control apparatus 1 of FIG. 2, the position corresponding to the LPM No. 2 valve 37). 2) and a clutch control valve 51 (selection valve) as a component corresponding to the manual valve 41 in the hydraulic control device 1 of FIG. 2 is different from the hydraulic control device 1 of the above embodiment. .
- the hydraulic control device 1a is connected to be able to communicate with a plurality of clutches related to the AT.
- the plurality of clutches are collectively shown as “C1 control system 52”.
- the clutch control valve 51 can selectively switch a clutch communicated with the clutch oil passage 38 from among the plurality of clutches in order to realize a desired gear ratio.
- a clutch pressure Pc1 is supplied to the clutch communicated with the clutch oil passage 38 by the clutch control valve 51. That is, in the hydraulic control apparatus 1a, the clutch control valve 51 functions as a selection valve that selects a clutch that supplies oil from the hydraulic path 33.
- the position where the second oil passage 47 is connected to the hydraulic passage 33 is downstream of the clutch control valve 51.
- the second oil passage 47 is connected at a position on the hydraulic passage 33 where the hydraulic pressure is the same level as the hydraulic pressure actually supplied to the C1 control system 52.
- connection control means for controlling the connection between the accumulator 44 and the hydraulic path 33
- the combination of the switching valve 48 and the pressure accumulation control valve 43 has been exemplified.
- the first oil path 46 and the second oil path Other configurations, such as a configuration in which each of 47 is provided with a control valve and one of the valves is opened, are also possible.
- the switching valve 48 switches the communication between the first oil passage 46 and the second oil passage 47 using the line pressure PL as the operating pressure.
- the switching valve 48 can be switched according to the driving / stopping of the engine 3. If possible, a pressure other than the line pressure may be used as the operating pressure.
- the hydraulic pressure Plpm2 of the clutch oil passage 38 is used as the hydraulic pressure introduced into the second back pressure chamber 44e of the accumulator 44.
- the hydraulic pressure generated according to the drive of the mechanical pump 31 is used.
- the line pressure PL may be introduced.
- the C1 clutch (the forward / reverse switching clutch C1 and the forward / reverse switching brake B1) of the forward / reverse switching mechanism 10 is illustrated as the clutch that is hydraulically controlled by the hydraulic control device 1, but this clutch is idling.
- the stop control is in an open state, the rotational torque between the engine and the drive wheel side can be cut off, and if it is in the engaged state and the drive wheel side rotational torque can be transmitted to the engine side, forward / reverse switching A clutch other than the C1 clutch of the mechanism 10 may be used.
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Abstract
Description
図1~8を参照して本発明の一実施形態について説明する。まず、図1を参照して、本実施形態に係る油圧制御装置1を搭載する車両2の構成について説明する。図1に示すように、この車両2は、走行時における動力源としてのエンジン3と、駆動輪4と、動力伝達装置5と、油圧制御装置1と、ECU(Electronic Control Unit:電子制御ユニット)7とを備える。
Fs=k・X ・・・(1)
ここで、kはスプリング44fのバネ定数であり、Xは保圧時における蓄圧室44cの高さである。
Pacc=Fs/As=k・X/As ・・・(2)
ここで、Asは小径側(図3、4では下方)の端面の面積である。
Vacc=As・X ・・・(3)
Fe=Pe・(Al-As) ・・・(4)
Fs’=k・h ・・・(5)
ここで、Alは段付ピストン44bの大径側(図3、4では上方)の端面の面積である。
h=Pe・(Al-As)/k ・・・(6)
Pdumper=Fc1/As
=(Fs-Fe)/As
=Pacc-Pe・(Al-As)/As
・・・(7)
Vdumper=Vacc-As・h
=Vacc-Pe・As・(Al-As)/k
・・・(8)
次に、図9を参照して本実施形態の変形例について説明する。上記実施形態では、変速装置の一例としてベルト式の無段変速機構11(CVT)を適用した場合について説明しているが、変速装置には、例えば有段自動変速機(AT)などの他の変速装置を用いてもよい。
2 車両
3 エンジン
7 ECU
18,52 C1制御系(クラッチ)
31 メカポンプ(機械ポンプ)
33 油圧経路
40 SLCリニアソレノイド(クラッチ圧制御弁)
41 マニュアルバルブ(選択バルブ)
43 蓄圧制御弁(接続制御手段)
44 アキュムレータ
46 第1油路
47 第2油路
48 切替弁(接続制御手段)
49 チェック弁
50 背圧制御用油路(第3油路)
51 クラッチコントロールバルブ(選択バルブ)
Claims (5)
- 車両のエンジンの駆動によりオイルを吐出する機械ポンプと、
前記機械ポンプにより吐出されたオイルをクラッチに供給する油圧経路と、
前記油圧経路上に設けられ、前記クラッチへ供給する油圧であるクラッチ圧を制御するクラッチ圧制御弁と、
前記油圧経路の前記クラッチ圧制御弁の下流に設けられ、前記油圧経路から前記オイルを供給するクラッチを選択する選択バルブと、
を備える油圧制御装置において、
前記機械ポンプにより供給されるオイルを蓄圧し、蓄圧されたオイルを吐出して前記クラッチに供給するアキュムレータと、
前記クラッチ圧制御弁より上流側にて前記油圧経路と接続される第1油路と、
前記選択バルブより下流側にて前記油圧経路と接続される第2油路と、
前記アキュムレータを前記第1油路及び前記第2油路の一方と連通するよう前記アキュムレータと前記油圧経路との接続を制御する接続制御手段と、
前記機械ポンプにより供給されるオイルを前記アキュムレータの背圧側へ供給する第3油路と、
を備えることを特徴とする油圧制御装置。 - 前記接続制御手段が、
前記エンジンの停止時には前記第1油路を介して前記アキュムレータを前記油圧経路と連通し、前記エンジンの運転時には前記第2油路を介して前記アキュムレータを前記油圧経路と連通するよう切り替える切替弁と、
前記切替弁と前記アキュムレータとの間に配置され、前記アキュムレータの蓄圧及び吐出を制御する蓄圧制御弁と、
を備えることを特徴とする、請求項1に記載の油圧制御装置。 - 前記油圧経路上の前記第1油路との接続位置より上流側に、前記油圧経路の上流側へのオイルの逆流を防止するチェック弁を備えることを特徴とする、請求項1または2に記載の油圧制御装置。
- 前記第3油路は、前記チェック弁より上流側にて前記油圧経路と接続されることを特徴とする、請求項3に記載の油圧制御装置。
- エンジンと、
クラッチと、
前記クラッチを作動させるために供給されるオイルの油圧を制御する請求項1~4に記載の油圧制御装置と、を備え、
車両走行中に前記エンジンを停止するエコラン制御を実行可能であることを特徴とする車両制御装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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EP12865248.4A EP2803881B1 (en) | 2012-01-11 | 2012-01-11 | Oil pressure control device and vehicle control device |
JP2013553137A JP5761380B2 (ja) | 2012-01-11 | 2012-01-11 | 油圧制御装置及び車両制御装置 |
PCT/JP2012/050396 WO2013105233A1 (ja) | 2012-01-11 | 2012-01-11 | 油圧制御装置及び車両制御装置 |
US14/239,026 US8986164B2 (en) | 2012-01-11 | 2012-01-11 | Hydraulic pressure control device and vehicle control device |
CN201280039632.8A CN104169615B (zh) | 2012-01-11 | 2012-01-11 | 油压控制装置以及车辆控制装置 |
Applications Claiming Priority (1)
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PCT/JP2012/050396 WO2013105233A1 (ja) | 2012-01-11 | 2012-01-11 | 油圧制御装置及び車両制御装置 |
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US (1) | US8986164B2 (ja) |
EP (1) | EP2803881B1 (ja) |
JP (1) | JP5761380B2 (ja) |
CN (1) | CN104169615B (ja) |
WO (1) | WO2013105233A1 (ja) |
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EP2784355B1 (en) | 2011-11-22 | 2017-12-20 | Toyota Jidosha Kabushiki Kaisha | Oil pressure control device |
KR101861457B1 (ko) * | 2014-02-20 | 2018-05-28 | 쟈트코 가부시키가이샤 | 유압 제어 장치, 및 그 제어 방법 |
CN105346537B (zh) * | 2015-12-01 | 2018-07-24 | 常州轻工职业技术学院 | 车辆启动、熄火、手刹联合控制系统 |
US10316962B2 (en) * | 2016-01-18 | 2019-06-11 | Ford Global Technologies, Llc | Vehicle transmission with accumulator |
CN107303856B (zh) * | 2016-04-25 | 2020-10-27 | 上海汽车集团股份有限公司 | 动力系统及车辆 |
DE102016218835A1 (de) * | 2016-09-29 | 2018-03-29 | Ford Global Technologies, Llc | Ölversorgungseinheit und Kraftfahrzeug |
JP6662471B2 (ja) * | 2016-11-24 | 2020-03-11 | 日産自動車株式会社 | 無段変速機の制御方法、及び、無段変速機システム |
JP6594381B2 (ja) * | 2017-08-10 | 2019-10-23 | 本田技研工業株式会社 | 油圧制御装置 |
CN107387598B (zh) * | 2017-08-24 | 2023-06-20 | 中国第一汽车股份有限公司 | 一种自动变速器高效油源系统 |
JP7115956B2 (ja) * | 2018-10-29 | 2022-08-09 | トヨタ自動車株式会社 | 車両用駆動装置の油圧制御回路 |
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- 2012-01-11 EP EP12865248.4A patent/EP2803881B1/en not_active Not-in-force
- 2012-01-11 US US14/239,026 patent/US8986164B2/en not_active Expired - Fee Related
- 2012-01-11 CN CN201280039632.8A patent/CN104169615B/zh not_active Expired - Fee Related
- 2012-01-11 JP JP2013553137A patent/JP5761380B2/ja not_active Expired - Fee Related
- 2012-01-11 WO PCT/JP2012/050396 patent/WO2013105233A1/ja active Application Filing
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Also Published As
Publication number | Publication date |
---|---|
EP2803881A1 (en) | 2014-11-19 |
JP5761380B2 (ja) | 2015-08-12 |
US8986164B2 (en) | 2015-03-24 |
CN104169615B (zh) | 2016-05-04 |
CN104169615A (zh) | 2014-11-26 |
EP2803881A4 (en) | 2016-04-20 |
JPWO2013105233A1 (ja) | 2015-05-11 |
US20140315687A1 (en) | 2014-10-23 |
EP2803881B1 (en) | 2018-02-28 |
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