WO2012111074A1 - 油圧回路およびその制御装置 - Google Patents
油圧回路およびその制御装置 Download PDFInfo
- Publication number
- WO2012111074A1 WO2012111074A1 PCT/JP2011/053051 JP2011053051W WO2012111074A1 WO 2012111074 A1 WO2012111074 A1 WO 2012111074A1 JP 2011053051 W JP2011053051 W JP 2011053051W WO 2012111074 A1 WO2012111074 A1 WO 2012111074A1
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- Prior art keywords
- pressure
- oil
- hydraulic
- filter
- valve
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- 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
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0402—Cleaning of lubricants, e.g. filters or magnets
- F16H57/0404—Lubricant filters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/615—Filtering means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7052—Single-acting output members
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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
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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
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
Definitions
- the present invention relates to a hydraulic circuit for supplying or discharging hydraulic pressure to a member that operates by hydraulic pressure, and a control device for controlling the hydraulic circuit, and in particular, a first circuit unit that is controlled in a state in which the hydraulic pressure is confined.
- the present invention relates to a hydraulic circuit and a control device therefor.
- hydraulic pressure is used as a means for transmitting power, or as a means for transmitting information on operating states.
- the hydraulic pressure generated by the pump is sent to a motor to drive the vehicle, or move or transport heavy objects.
- the hydraulic pressure is used as a control signal for adjusting the hydraulic pressure supplied to an actuator such as a motor, or for supplying or blocking the hydraulic pressure.
- EP 0 985 855 An example of this type of hydraulic circuit in a vehicle is described in EP 0 985 855.
- the vehicle described in the specification of European Patent No. 0985855 is a vehicle equipped with a belt-type continuously variable transmission, and an oil pump driven by a motor and an oil pump generated in the hydraulic circuit thereof An accumulator that stores the hydraulic pressure, and supplies the hydraulic pressure from the oil pump and the accumulator to the hydraulic chambers of the primary pulley and the secondary pulley, and appropriately controls the supplied hydraulic pressure to obtain a predetermined gear ratio. While setting, it is comprised so that the target clamping pressure may be set. Further, the hydraulic control device described in the specification of European Patent No.
- 0985855 is configured to supply and discharge hydraulic pressure to and from the primary pulley and the secondary pulley by an electrically controlled electromagnetic valve.
- the solenoid valve By energizing and opening the solenoid valve, the hydraulic pressure is supplied to the primary pulley for upshifting, and the hydraulic pressure is supplied to the secondary pulley to increase the clamping pressure.
- the hydraulic pressure By energizing and opening it, the hydraulic pressure is discharged from the primary pulley to downshift, and the hydraulic pressure is discharged from the secondary pulley to reduce the clamping pressure. Therefore, by controlling all the electromagnetic valves to the closed state, the hydraulic pressure is closed in the hydraulic chambers of the primary pulley and the secondary pulley, so that a predetermined gear ratio and belt clamping pressure can be maintained.
- transmission oil mounted on a vehicle may be used for lubrication. Since the lubricating oil is supplied to the frictional contact portion to form an oil film, impurities or contaminants such as metal powder or carbon powder may be mixed in the lubricating oil. Therefore, for example, a continuously variable transmission described in Japanese Patent Application Laid-Open No. 2008-144830 is configured to supply lubricating oil to a toroidal transmission mechanism through a filter.
- Japanese Patent Application Laid-Open No. 5-184212 discloses a device in which an oil pump is configured to suck oil through a filter.
- the hydraulic pressure pumped up by a single oil pump is the hydraulic chamber of the actuator or primary pulley and secondary pulley described above.
- it is necessary to keep the oil pump driven at all times because it is constantly or continuously supplied to the bearings, clutches, gears, etc., which may further increase power loss. There is.
- An object of the present invention is to provide a hydraulic circuit capable of reducing power loss and a control device therefor.
- the present invention provides a first circuit portion having a pressure accumulating portion for accumulating oil pressure, a control valve for opening and closing an oil passage for supplying oil pressure from the pressure accumulating portion to a predetermined actuator, and the pressure accumulating portion
- a hydraulic circuit comprising an oil pump that supplies hydraulic pressure to a hydraulic circuit and a second circuit portion that continuously supplies pressure oil discharged from the oil pump, the pressure oil supplied to the second circuit portion
- a first filter that removes foreign matters smaller than the mixed foreign matters from the pressure oil supplied to the pressure accumulating section is provided.
- the first filter is provided in the middle of another oil passage that branches from an oil passage that supplies pressure oil from the oil pump to the second circuit portion and supplies pressure oil to the pressure accumulation portion. It is the hydraulic circuit characterized by being provided.
- control valve includes a supply valve that opens and closes the oil passage that supplies hydraulic pressure from the pressure accumulator to the actuator, and a discharge valve that discharges pressure from the actuator.
- the valve body may be pressed against the valve seat to seal the port.
- the actuator can include a hydraulic chamber of an automatic transmission that changes a gear ratio when hydraulic pressure is supplied or hydraulic pressure is discharged.
- the pressure accumulating section can be configured to store a higher hydraulic pressure than the hydraulic pressure supplied to the second circuit section.
- the actuator is configured to reduce a width of the belt winding groove and increase a belt winding radius by supplying hydraulic pressure, and a hydraulic ratio chamber.
- the second circuit section continuously lubricates the pressure oil discharged from the oil pump to perform lubrication.
- a hydraulic circuit including a lubrication part.
- the present invention in any one of the above-described inventions, further includes a second filter that removes foreign matters by passing the pressure oil sucked by the oil pump or the pressure oil discharged by the oil pump, and the first filter
- the hydraulic circuit is characterized in that the roughness of the eyes is finer than that of the second filter.
- the present invention provides the method according to any one of the above-described aspects, wherein the oil path is provided in the middle of the oil path that supplies pressure oil from the oil pump to the pressure accumulating unit, and the oil path is switched between a communication state and a shut-off state
- the hydraulic circuit further includes one open / close valve.
- the first on-off valve may be constituted by a switching valve that selectively switches between a state in which the oil passage is communicated and a state in which the oil passage is cut off, and a discharge pressure state in which the pressure accumulating portion is in communication with the drain location.
- This invention is the invention according to any one of the above-mentioned inventions, wherein a bypass oil passage that bypasses the first filter provided in the middle of the oil passage that supplies pressure oil from the oil pump to the pressure accumulating section, and the bypass
- the hydraulic circuit further includes a second opening / closing valve that opens and closes the oil passage.
- the present invention is the control device for any of the hydraulic circuits described above, further comprising foreign matter removing means for separating the foreign matter captured by the first filter from the first filter. To do.
- the control apparatus is characterized in that, in the above configuration, the foreign matter removing means includes means for flowing pressure oil from the pressure accumulating section side to the second circuit side with respect to the first filter.
- a circuit control device includes means for flowing pressure oil from the pressure accumulating section side to the second circuit side with respect to the first filter.
- the control device is the control device for any one of the hydraulic circuits described above, wherein the hydraulic pressure of the pressure accumulating unit is higher than the discharge pressure of the oil pump or the hydraulic pressure on the second circuit side.
- Foreign matter removing means is provided for switching the first on-off valve so that the oil passage is in communication, and for removing the foreign matter captured by the first filter from the first filter.
- the control device is the control device for the hydraulic circuit described above, wherein the foreign matter captured by the first filter by switching the switching valve so as to communicate the pressure accumulating portion with the drain location is provided. It is characterized by having a foreign substance removing means for separating from the body.
- the foreign matter removing means includes means for operating the foreign matter to be removed from the first filter at a predetermined time interval. It is the control apparatus of the hydraulic circuit characterized by including.
- control device is a control device for a hydraulic circuit having the above-described configuration, and is provided in the middle of the oil passage for supplying pressure oil from the oil pump to the pressure accumulating section.
- a first on-off valve that switches between a communication state and a shut-off state, and when the hydraulic pressure of the pressure accumulator is higher than the discharge pressure of the oil pump or the hydraulic pressure on the second circuit side and the clamping pressure is equal to or higher than a predetermined pressure
- a foreign matter removing means for switching the first on-off valve so that the oil passage is in a communicating state and for removing the foreign matter captured by the first filter from the first filter. It is.
- control apparatus of this invention is a control apparatus of the hydraulic circuit mentioned above, Comprising: It is provided in the middle of the said oil path which supplies pressure oil to the said pressure accumulation part from the said oil pump, and the state which connects the said oil path A switching valve that switches between a state that shuts off and a state that communicates with the drain location; and the switching valve that switches the switching valve to communicate with the drain location when the clamping pressure is equal to or higher than a predetermined pressure.
- Foreign matter removing means for separating the foreign matter captured by one filter from the first filter is further provided.
- the pressure oil discharged from the oil pump is supplied to the first circuit portion and the second circuit portion including the pressure accumulating portion, but continuously to the second circuit portion, or While the pressure oil is always supplied, the pressure oil is supplied when the pressure in the pressure accumulating portion is reduced with respect to the first circuit portion.
- the oil pressure is supplied through a first filter that captures foreign matters smaller than the foreign matter mixed in the pressure oil supplied to the second circuit portion. Therefore, although the flow resistance is relatively large, since the hydraulic pressure is not always supplied to the first circuit portion, the power loss increases even if the flow resistance by the first filter is relatively large. Can be prevented or suppressed.
- the control oil and the actuator using the pressure accumulating portion as a hydraulic source have pressure oil from which the foreign matter is sufficiently and sufficiently removed.
- a so-called hydraulic confinement state can be established, so that power loss can also be prevented or suppressed in this respect.
- the flow resistance to the hydraulic pressure supplied to the control valve, actuator, etc. is reduced and the hydraulic response is improved. Can do.
- the present invention is applied to a hydraulic circuit that supplies and discharges hydraulic pressure to / from a hydraulic chamber that controls the gear ratio in the automatic transmission, the fuel efficiency of a vehicle equipped with the automatic transmission can be improved.
- the present invention to the hydraulic circuit of the belt type continuously variable transmission, the fuel efficiency of the vehicle equipped with the belt type continuously variable transmission can be improved.
- the roughness of the second filter is greater than the roughness of the first filter. Even if the hydraulic pressure is supplied continuously or constantly to the second circuit portion because it is rough, the flow resistance due to the second filter is relatively small, so that power loss can be reduced or prevented.
- the oil passage for supplying pressure oil from the oil pump to the pressure accumulating portion is closed by the first opening / closing valve, the oil pressure from the oil pump to the pressure accumulating portion or the first circuit portion is stopped. Further, it is possible to prevent the hydraulic pressure from leaking from the pressure accumulating section or the first circuit section toward the second circuit section, and to control the first circuit section using the pressure accumulating section as a hydraulic pressure source.
- the so-called reverse flow of the pressure oil to the first filter causes the foreign matter captured by the first filter to be separated from the first filter. be able to.
- the first open / close valve is configured by a switching valve that allows the pressure accumulating portion to communicate with the drain location
- the pressure at the drain location is lower than the hydraulic pressure of the pressure accumulating portion.
- the pressure oil can be reversely flowed, and the foreign matter separated from the first filter can be discharged to the drain location.
- a bypass oil passage that bypasses the first filter is provided, and the bypass oil passage can be opened and closed by the second opening / closing valve. Therefore, when it is necessary to rapidly supply hydraulic pressure from the oil pump toward the pressure accumulating part or the first circuit part, the pressure accumulating part is not subjected to resistance by the first filter by opening the second on-off valve. In addition, the hydraulic pressure can be rapidly supplied to the first circuit portion.
- control apparatus while controlling a hydraulic circuit as mentioned above, while removing a foreign substance from the pressure oil supplied with respect to a 1st circuit part, clogging of the 1st filter for that purpose
- the increase in flow resistance or the loss of power associated therewith can be reduced.
- FIG. 1 is a hydraulic circuit diagram schematically showing a specific example of the present invention. It is a flowchart for demonstrating an example of the control which removes a foreign material from a sub filter. It is a flowchart for demonstrating the other example of control which removes a foreign material from a sub filter.
- FIG. 6 is a hydraulic circuit diagram schematically showing another specific example of the present invention.
- FIG. 6 is a hydraulic circuit diagram schematically showing still another specific example of the present invention. It is a schematic diagram which shows an example of the automatic transmission which can be made into object by this invention.
- a hydraulic circuit according to the present invention includes a first circuit unit having a pressure accumulating unit as a hydraulic source, an oil pump for generating hydraulic pressure to be supplied to the pressure accumulating unit, and an oil pump And a second circuit portion to which oil pressure is continuously supplied from the oil pump when operating.
- the reason why at least two circuit portions are provided is that the pressure and amount of the hydraulic pressure required for each circuit portion are different, and an example of such a hydraulic circuit is a belt type. It is a hydraulic circuit of the automatic transmission for vehicles provided with the continuously variable transmission.
- FIG. 6 schematically shows an example of an automatic transmission for a vehicle including a belt-type continuously variable transmission.
- a driving force source 1 shown here is an internal combustion engine such as a gasoline engine, an electric motor, or these internal combustion engine and electric motor. So-called hybrid type. In the following description, an example in which an engine is employed as the driving force source 1 will be described. Therefore, the driving force source 1 is referred to as the engine 1.
- a torque converter (T / C) 2 is connected to the output side of the engine 1.
- This torque converter 2 has a general structure widely used in vehicles, and includes a direct coupling clutch (lock-up clutch) 3 that directly connects an input side element and an output side element.
- a forward / reverse switching mechanism 4 is arranged following the torque converter 2.
- the forward / reverse switching mechanism 4 may be of any configuration as long as it can output the input torque as it is, and can output the torque by reversing the direction of the torque.
- the forward / reverse switching mechanism 4 is mainly composed of a double pinion type planetary gear mechanism.
- a ring gear 6 that is an internal gear is arranged concentrically with the sun gear 5 connected to the output element of the torque converter 2, and the pinion gear meshed with the sun gear 5 is between the sun gear 5 and the ring gear 6.
- 7 and another pinion gear 8 meshing with the pinion gear 7 and the ring gear 6 are arranged, and these pinion gears 7 and 8 are held by the carrier 9 so that they can rotate and revolve.
- a clutch C1 for setting a forward state in which the torque input to the sun gear 5 is output as it is is provided.
- the clutch C1 is essentially a clutch configured to connect any two elements in the above-described double pinion type planetary gear mechanism and rotate the entire planetary gear mechanism integrally, as shown in FIG.
- the sun gear 5 and the carrier 9 are selectively connected.
- the clutch C1 can be constituted by a wet multi-plate clutch, and therefore, a plurality of friction plates and plates and hydraulic chambers (or hydraulic actuators) (not shown respectively) for bringing them into close contact with each other. It has.
- a brake B1 is provided for setting a reverse state in which the direction of torque input to the sun gear 5 is reversed and output.
- the brake B ⁇ b> 1 is configured to selectively connect the ring gear 6 to a fixed part 10 such as a casing and apply a reaction force to the ring gear 6 to stop its rotation.
- the brake B1 is specifically a wet multi-plate type, and includes a plurality of friction plates and plates and hydraulic chambers (or hydraulic actuators) (not shown) for bringing them into close contact with each other. I have. Therefore, in the example shown in FIG.
- the sun gear 5 is an input element
- the ring gear 6 is a reaction element
- the carrier 9 is an output element
- the clutch C1 is engaged and the sun gear 5 and the carrier 9 are connected.
- the entire planetary gear mechanism rotates as a unit, the torque input from the sun gear 5 and the carrier 9 is output as it is, and the forward state is set.
- the ring gear 6 is fixed by engaging the brake B1 instead of the clutch C1, and as a result, the carrier 9 rotates in the opposite direction with respect to the sun gear 5, so that the torque acting in the opposite direction to the input torque. Is output and the reverse state is set.
- a belt type continuously variable transmission 11 is connected to the output side of the forward / reverse switching mechanism 4 described above.
- the belt-type continuously variable transmission 11 has a configuration that is widely known in the past, and includes a pair of pulleys 12 and 13 each composed of a fixed sheave and a movable sheave disposed opposite thereto.
- a belt 14 is wound around a so-called V groove formed by a fixed sheave and a movable sheave.
- One pulley 12 is a driving pulley (primary pulley), and this primary pulley 12 is connected to the carrier 9 in the forward / reverse switching mechanism 4 described above.
- a hydraulic chamber (actuator) 15 is provided on the back side of the movable sheave in the primary pulley 12, and the width of the V-groove is increased by increasing the hydraulic pressure supplied to the hydraulic chamber 15 or increasing the amount of pressurized oil.
- the belt 14 is configured to be narrower and increase the winding radius of the belt 14. That is, the example shown in FIG. 6 is configured to change the gear ratio by controlling the hydraulic pressure or the amount of pressure oil of the primary pulley 12.
- the other pulley 13 is a driven pulley (secondary pulley), and a hydraulic chamber (actuator) 16 is provided on the back side of the movable sheave.
- the belt 14 is driven by the hydraulic pressure supplied to and discharged from the hydraulic chamber 16. And a clamping pressure for setting a predetermined transmission torque capacity is generated.
- An output gear 18 provided on the pulley shaft 17 of the secondary pulley 13 meshes with a counter driven gear 19, and a counter drive gear 20 that rotates together with the counter driven gear 19 is a differential that forms a final reduction gear. It meshes with the ring gear 22 of the gear 21 and is configured to transmit torque from the differential gear 21 to left and right drive wheels (not shown).
- the lockup clutch 3, the clutch C1, the brake B1, the continuously variable transmission 11 and the like are configured to be controlled by hydraulic pressure, and a hydraulic control device 23 is provided for the control.
- the hydraulic control device 23 includes a plurality of electrically controlled valves, and engages the lock-up clutch 13, the clutch C 1, or the brake B 1 with hydraulic pressure that is output according to the on / off state of these valves.
- the gear ratio set by the continuously variable transmission 11 is changed, or the belt clamping pressure is changed to high or low. The specific configuration will be described later.
- an electronic control unit (ECU) 24 is provided for controlling the gear ratio and the belt clamping pressure and for controlling the supply and discharge of hydraulic pressure to and from the clutch C1 and the brake B1.
- the electronic control unit 24 is mainly composed of a microcomputer, and is configured to perform a calculation based on input data or data stored in advance and output a control command signal. Further, the electronic control unit 24 is configured to control the output of the engine 1, and accordingly, a control command signal is output from the electronic control unit 24 to the hydraulic control unit 23 and the engine 1 described above. Has been.
- a hydraulic circuit is provided with a supply electromagnetic valve and a discharge electromagnetic valve for each of the hydraulic chamber 15 in the primary pulley 12 and the hydraulic chamber 16 in the secondary pulley 13.
- a solenoid valve for supply and a solenoid valve for exhaust pressure are provided for the clutch C1 and the brake B1 described above, and these solenoid valves are electrically controlled to be opened and closed to control the gear ratio and transmission torque capacity.
- the hydraulic circuit shown here has an oil pump (so-called mechanical pump) 27 that is driven by the engine 1 to pump up and discharge oil from an oil pan 26.
- the suction port of the oil pump 27 communicates with a main filter Fa corresponding to the second filter in the present invention.
- the main filter Fa is for capturing foreign matter (contamination) such as metal powder or carbon powder mixed in the oil and removing it from the oil.
- the roughness (mesh) is set so as to remove foreign substances having a size that hinders the torque converter 2 or the hydraulic equipment for its control.
- a pressure regulating valve 28 such as a primary regulator valve for regulating the discharge pressure is connected to the discharge port of the oil pump 27.
- the pressure regulating valve 28 opposes the output pressure (discharge pressure of the oil pump 27) and the signal pressure across the spool, so that the pressure regulation level is increased according to the signal pressure, and the output pressure is increased. It is comprised so that it may become.
- the signal pressure is configured to be output from a discharge pressure control valve 29 including an electromagnetic valve such as a linear solenoid valve, and the discharge pressure control valve 29 is configured to be controlled by the electronic control device 24 described above. ing.
- the pressure regulating valve 28 is configured to perform pressure regulation by operating so as to balance the opposing load (hydraulic pressure) across the spool, drain hydraulic pressure is generated along with pressure regulation, and the drain
- a low pressure control circuit 31 is provided that controls the hydraulic pressure and supplies the torque converter 2 and various lubrication points 30 described above. Therefore, the low-pressure control circuit 31 includes a plurality of hydraulic control devices such as a regulator valve, a modulator valve, a switching valve, and an opening / closing valve. These low-pressure control circuit 31, torque converter 2, lubrication point 30, and the like that function using the drain hydraulic pressure generated from the pressure regulating valve 28 correspond to the second circuit portion 32 in the present invention.
- the accumulator 34 corresponding to the pressure accumulating portion in the present invention is connected to the discharge port of the oil pump 27 via the oil passage 33.
- An opening / closing valve 35 is provided in the middle of the oil passage 33 to switch the oil passage 33 between a communication state and a shut-off state (that is, open / close).
- the on-off valve 35 can be constituted by a solenoid valve, for example, and can be electrically switched between an open state and a closed state.
- a sub-filter Fb corresponding to the first filter in the present invention is provided between the opening / closing valve 35 and the accumulator 34.
- the sub-filter Fb has a finer mesh than the main filter Fa described above, captures foreign matter that is smaller than foreign matter mixed in the pressure oil supplied to the second circuit portion 32, and supplies it to the accumulator 34. Is configured to be removed from the pressurized oil.
- the accumulator 34 serves as a hydraulic pressure source for controlling the continuously variable transmission 11, the clutch C1, or the brake B1, and a pressure accumulation control valve 36 that is electrically controlled to open and close is connected to the inflow / outlet thereof.
- the opening / closing valve 35 separates the above-described second circuit portion 32 and the first circuit portion 37 that functions at a high pressure such as the continuously variable transmission 11.
- the pressure accumulation control valve 36 is configured to be controlled by the electronic control device 24 described above, and a hydraulic pressure sensor 38 for detecting the hydraulic pressure of the accumulator 34 and transmitting a detection signal to the electronic control device 24 is provided. It has been.
- the hydraulic pressure is supplied from the oil passage 39 branched between the pressure accumulation control valve 36 and the opening / closing valve 35 to the continuously variable transmission 11, the clutch C1, or the brake B1. More specifically, a supply electromagnetic valve 41 is provided in an oil passage 40 extending from the oil passage 39 to the hydraulic chamber 15 of the primary pulley 12, and the oil passage 40 is opened and closed by the supply electromagnetic valve 41.
- the pressure oil is selectively supplied to the hydraulic chamber 15 in the primary pulley 12.
- the hydraulic chamber 15 in the primary pulley 12 is connected to an electromagnetic valve 42 for exhaust pressure that discharges the hydraulic pressure in the hydraulic chamber 15 to a drain location such as the oil pan 26.
- the exhaust pressure electromagnetic valve 42 is connected to the oil passage 40 between the supply electromagnetic valve 41 and the hydraulic chamber 15.
- These supply electromagnetic valve 41 and exhaust pressure electromagnetic valve 42 are valves that are electrically controlled to open and close the ports, and are so-called poppet type valves that close the ports by pressing the valve body against the valve seat. Particularly in the non-energized state (off state), the port is closed with almost no hydraulic leakage. This is because even when the energization is interrupted, the hydraulic pressure is closed in the hydraulic chamber 15 to ensure a predetermined gear ratio and transmission torque capacity.
- the hydraulic pressure supply / discharge mechanism for the hydraulic chamber 16 in the secondary pulley 13 that sets the belt clamping pressure is configured similarly to the hydraulic supply / discharge mechanism for the hydraulic chamber 15 in the primary pulley 12 described above. That is, a supply electromagnetic valve 44 is provided in an oil passage 43 extending from the oil passage 39 to the hydraulic chamber 16 of the secondary pulley 13, and the oil passage 43 is opened and closed by the supply electromagnetic valve 44 in the secondary pulley 13. The hydraulic pressure is selectively supplied to the hydraulic chamber 16.
- the hydraulic chamber 16 in the secondary pulley 13 is in communication with an exhaust pressure electromagnetic valve 45 that discharges the hydraulic pressure in the hydraulic chamber 16 to a drain location such as the oil pan 26. In the example shown in FIG. 1, the exhaust pressure electromagnetic valve 45 is connected to the oil passage 43 between the supply electromagnetic valve 44 and the hydraulic chamber 16.
- These supply solenoid valve 44 and exhaust pressure solenoid valve 45 are electrically controlled valves that open and close the port, and are so-called poppet type valves that close the port by pressing the valve body against the valve seat. Particularly in the non-energized state (off state), the port is closed with almost no hydraulic leakage. This is because the hydraulic pressure is closed in the hydraulic chamber 16 to ensure a predetermined gear ratio and transmission torque capacity even when the energization is interrupted.
- a supply electromagnetic valve 47 is provided in an oil passage 46 from the oil passage 39 to the clutch C1, and the oil passage 46 is opened and closed by the supply electromagnetic valve 47 to supply hydraulic pressure to the hydraulic chamber in the clutch C1. Is to be done selectively.
- An exhaust pressure electromagnetic valve 48 is connected to the hydraulic chamber of the clutch C1.
- This solenoid valve 48 for exhaust pressure is a poppet type valve similar to the above-described solenoid valve for supply 47, and is configured to exhaust pressure from the clutch C1 to the drain location etc. electrically controlled.
- the supply electromagnetic valves 47 and 48 are configured to close the port with almost no leakage of hydraulic pressure in a non-energized state (off state).
- each electromagnetic valve 41, 42, 44, 45, 47, 48, etc. shown in FIG. 1 is configured to be controlled by the electronic control device 24.
- the oil pump 27 is driven by the power to discharge the hydraulic pressure.
- the discharge pressure is regulated to an appropriate pressure by the pressure regulating valve 28.
- the discharge pressure control valve 29 is controlled by the electronic control unit 24 to output a signal pressure of a predetermined pressure, which is supplied to the pressure regulation valve 28 and has a pressure regulation level corresponding to the signal pressure.
- the pressure adjustment is performed while discharging the drain hydraulic pressure, and the drain hydraulic pressure is supplied to the torque converter 2 and the lubrication point 30 via the low pressure control circuit 31.
- the hydraulic pressure adjusted to a high pressure by the pressure adjusting valve 28 is higher than the hydraulic pressure of the high-pressure side circuit such as the oil passage 39, the hydraulic pressure is supplied to the oil passage 39 side when the opening / closing valve 35 is opened.
- pressure is accumulated in the accumulator 34. Accumulation in the accumulator 34 is executed when the pressure drops below a predetermined pressure.
- the pressure oil discharged from the oil pump 27 is supplied to the accumulator 34 through the oil passage 33 and is By passing through the filter Fb, foreign matters larger than the roughness of the eyes are captured by the sub-filter Fb and removed from the pressure oil. That is, the pressure oil supplied to the first circuit unit 37 is clean and does not include foreign matters larger than the coarseness of the sub-filter Fb.
- the hydraulic pressure stored in the accumulator 34 is supplied to the first circuit portion 37 by opening the pressure accumulation control valve 36 with the open / close valve 35 closed. Control of the gear ratio and clamping pressure of the continuously variable transmission 11 or the engagement / release of the clutch C1 is executed by the hydraulic pressure supplied in this way.
- the supply electromagnetic valve 41 for the primary pulley 12 is opened and hydraulic pressure is supplied to the hydraulic chamber 15 of the primary pulley 12, and the groove width is narrowed.
- the winding radius of the belt 14 with respect to the secondary pulley 13 decreases and the transmission ratio decreases.
- each electromagnetic valve 41, 42, 44, 45, 47, 48 is maintained in a closed state. That is, the hydraulic pressure is confined in the actuators such as the hydraulic chambers 15 and 16.
- the electromagnetic valves 41, 42, 44, 45, 47, and 48 that perform such closing control are so-called poppet type valves that maintain the closed state by pressing the valve body against the valve seat. Since the pressure oil passing through 41, 42, 44, 45, 47, and 48 is clean with the foreign matter removed as described above, the foreign matter that has a gap between the valve seat and the valve body is removed. There is no biting. For this reason, there is no possibility of leaking high oil pressure when the closing control is performed, and power loss due to oil pressure leakage can be prevented or reduced.
- the oil pump 27 is driven by the engine 1 to discharge the hydraulic pressure, the torque converter 2 rotates, and further the lubrication point At 30, slipping occurs. Therefore, when it is not necessary to supply hydraulic pressure to the accumulator 34 or the first circuit portion 37, the pressure regulating valve 28 regulates the discharge pressure of the oil pump 27 to a low pressure, and the drain hydraulic pressure accompanying the pressure regulation is the second circuit.
- the unit 32 is continuously supplied. In this way, the pressure oil supplied to the second circuit portion 32 side has foreign matters removed by the main filter Fa, but the coarseness of the main filter Fa is such that it is used in a normal hydraulic circuit. Since the flow resistance is not particularly large, excessive power loss does not occur.
- the pressure oil is continuously or constantly supplied to the second circuit portion 32, but the oil pressure may be supplied to the first circuit portion 37 only when accumulating pressure.
- the pump 27 can have a small discharge capacity. That is, the oil pump 27 can be reduced in size. By doing so, an unnecessary large amount of pressure oil is not drained, so that power loss can be reduced, and consequently the fuel efficiency of the vehicle can be improved.
- This separation / removal process is performed by opening the pressure accumulating electromagnetic valve 36 and the opening / closing valve 35 in a state where the hydraulic pressure of the accumulator 34 is higher than the discharge pressure of the oil pump 27, that is, the hydraulic pressure regulated by the pressure regulating valve 28.
- the control means for causing the pressure oil to flow backward to the sub-filter Fb corresponds to the foreign matter removing means in the present invention, and the control can be performed by the electronic control device 24 described above, and an example of the control is shown in FIG. FIG. 3 is a flowchart.
- FIG. 2 shows an example of control when the engine 1 is started and when the engine 1 is stopped.
- the belt clamping pressure is set by the hydraulic pressure in the hydraulic chamber 16 of the secondary pulley 13. Therefore, the determination in step S1 can be made by detecting the hydraulic pressure in the hydraulic chamber 16 of the secondary pulley 13 and comparing it with the target pressure.
- the target pressure is a pressure corresponding to the required driving force for the vehicle, and a format such as a map can be determined in advance.
- the determination in step S1 is a determination step performed in order to avoid belt slipping. Therefore, if the negative determination is made in step S1 because the belt clamping pressure has not reached the target pressure, control is performed in particular. Instead, the routine shown in FIG. In a case where an affirmative determination is made in step S1 by the belt clamping pressure on the opposite it has reached the target pressure thereto, or high pressure or not from hydraulic pressure Pac in the accumulator 34 is a hydraulic P 32 of the second circuit portion 32 Is determined (step S2). Since the hydraulic sensor 38 is connected to the accumulator 34, the determination in step S2 can be made based on the detection value of the hydraulic sensor 38.
- step S2 Since it is necessary for the hydraulic pressure of the accumulator 34 to be high in order to cause the pressure oil to flow backward to the sub-filter Fb, when a negative determination is made in step S2, there is no particular control in FIG. The routine shown is temporarily terminated. On the contrary, if the accumulator 34 has a high hydraulic pressure and is determined to be affirmative in step S2, an open command signal for opening the above-described open / close valve 35 is output (step S3).
- the accumulating electromagnetic valve 36 may be controlled to open together with the opening / closing valve 35.
- the pressure oil is passed from the accumulator 34 through the oil passage 33 to the second circuit portion 32 side or the oil pump 27 side in a state where the belt clamping pressure is sufficiently and sufficiently secured. Since it flows, the pressure oil flows backward to the sub-filter Fb, and the foreign matter captured by the sub-filter Fb is separated from the sub-filter Fb and removed. The foreign matter is mixed into the pressure oil flowing toward the second circuit portion 32, but the size of the foreign matter is small enough not to cause a problem in the second circuit portion 32. No abnormality is caused in each device constituting the unit 32.
- the control example shown in FIG. 3 is a control example that is executed in a normal time when the belt-type continuously variable transmission 11 is stably operating due to, for example, the vehicle running steady, and foreign matter is removed from the sub-filter Fb. It is determined whether or not a predetermined time has passed in advance from the previous operation that has been removed and removed (step S11).
- the predetermined time is a time until the amount of foreign matter captured by the sub-filter Fb becomes an obstacle to the control of the hydraulic pressure or a shorter time, and can be determined by an experiment or simulation using an actual machine. If it is determined negative in step S11 because the elapsed time from the previous operation is short, the routine shown in FIG. 3 is temporarily terminated without performing any particular control.
- step S11 hydraulic Pac the accumulator 34 or the high pressure or not is determined from the hydraulic pressure P 32 of the second circuit section 32 (step S12). This is the same control as the control in step S2 shown in FIG. Therefore, if a negative determination is made in step S12, the routine shown in FIG. 3 is temporarily terminated without performing any particular control.
- step S12 an open command signal for opening the on-off valve 35 described above is output (step S13).
- the accumulating electromagnetic valve 36 may be controlled to open together with the opening / closing valve 35.
- pressure oil flows from the accumulator 34 through the oil passage 33 to the second circuit portion 32 side or the oil pump 27 side at regular intervals.
- the pressure oil flows backward, so that the foreign matter captured by the sub-filter Fb is separated from the sub-filter Fb and removed.
- the foreign material will mix in the pressure oil which flows toward the 2nd circuit part 32, it does not cause abnormality in each apparatus which comprises the 2nd circuit part 32 because of the foreign material. This is the same as when the control shown in FIG. 2 is performed.
- the sub-filter Fb provided for removing foreign substances from the pressure oil supplied to the first circuit part 37 side has a fine mesh, so that the oil pump 27 to the first circuit part 37 are fine.
- a flow resistance is generated with respect to the pressure oil supplied toward the pressure, and the flow resistance increases as the flow speed of the pressure oil increases.
- a configuration as shown in FIG. be able to.
- the example shown in FIG. 4 is an example in which, in the configuration shown in FIG. 1 described above, a bypass oil passage 49 and an opening / closing valve 50 for opening and closing the bypass oil passage 49 are provided for the sub-filter Fb.
- the open / close valve 50 is an electromagnetic valve configured to be electrically controlled to open and close the oil passage, similar to the open / close valve 35 provided on the upstream side (oil pump 27 side) of the sub-filter Fb. It may be.
- the opening / closing valve 50 is controlled to be in an open state when it is necessary to change the gear ratio rapidly, for example, when an accelerator pedal (not shown) of the vehicle is rapidly depressed or the vehicle speed is rapidly decreased. Normally, it is kept closed.
- Such control is configured so that, for example, the accelerator opening is detected by a sensor (not shown), the change rate of the accelerator opening is obtained based on the detection signal, and the change is performed when the change rate exceeds a threshold value. do it.
- the vehicle speed may be detected, and the opening / closing valve 50 may be controlled to open when the rate of change of the vehicle speed (that is, acceleration / deceleration) exceeds a threshold value.
- the valve arranged in series with respect to the sub filter Fb can be constituted by a three-way valve.
- An example thereof is shown in FIG. 5, and an electromagnetic three-way valve 51 is provided on the upstream side (the oil pump 27 side) of the sub-filter Fb in the oil passage 33 that connects the oil pump 27 and the accumulator 34. .
- the electromagnetic three-way valve 51 closes the oil passage 33 between the oil pump 27 and the sub-filter Fb when the oil passage 33 is in communication, that is, the oil pump 27 and the sub-filter Fb or the accumulator 34 are in communication.
- a solenoid valve configured to switch between three states, that is, a state in which the valve is closed (blocked) and a state in which the upstream side of the sub-filter Fb is connected to a drain location such as the oil pan 26, and the electronic control unit 24. It is comprised so that it may be controlled by.
- the electromagnetic three-way valve 51 since the electromagnetic three-way valve 51 is provided, the above-described pressure accumulating electromagnetic valve 36 is not provided, and the accumulator 34 is directly communicated with the sub filter Fb.
- the electromagnetic three-way valve 51 is controlled in a state in which the oil passage 33 is closed in a state in which the vehicle is traveling steady or quasi-steady and the necessary and sufficient hydraulic pressure is accumulated in the accumulator 34.
- the first circuit unit 37 is controlled using the accumulator 34 as a hydraulic pressure source.
- the discharge pressure of the oil pump 27 is controlled to a pressure as low as required by the second circuit portion 32, so that power consumption by the oil pump 27 is reduced.
- the discharge pressure of the oil pump 27 is increased, and the electromagnetic three-way valve 51 is switched to a state in which the sub filter Fb communicates with the drain location.
- the foreign matter captured by the sub-filter Fb can be discharged directly to the drain location. Further, since the pressure at the drain location is about atmospheric pressure and is always lower than the hydraulic pressure of the accumulator 34, the detachment / removal of the foreign matter from the sub-filter Fb can be executed at an arbitrary time.
- the electromagnetic three-way valve 51 corresponds to the switching valve in the present invention.
- a fine sub-path is provided in the middle of the oil passage that branches from the oil passage that continuously supplies the pressure oil from the oil pump 27 to the second circuit portion 32 and supplies the pressure oil to the accumulator 34.
- a filter Fb is provided. The point is to remove finer foreign matters mixed in the pressure oil stored in the accumulator 34. Accordingly, the position where the sub-filter Fb is provided in the present invention is appropriately selected within the range of achieving the purpose. For example, when the oil pump 27 or an appropriate switching valve connected to the discharge side thereof has two ports, the sub-filter Fb may be provided on the discharge side of the port communicating with the accumulator 34. In the example shown in FIG. 1 or FIG.
- the opening / closing valve 35 is provided on the upstream side of the sub-filter Fb.
- the opening / closing valve 35 is provided on the downstream side of the sub-filter Fb, that is, on the accumulator 34 side. Also good.
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Abstract
Description
Claims (17)
- 油圧を蓄える蓄圧部とその蓄圧部から所定のアクチュエータに油圧を供給する油路を開閉する制御バルブとを有する第一回路部と、その蓄圧部に対して油圧を供給するオイルポンプと、そのオイルポンプから吐出された圧油を連続的に供給する第二回路部とを備えた油圧回路において、
前記第二回路部に供給される圧油に混入している異物より小さい異物を前記蓄圧部に供給される圧油から除去する第一フィルタを備えていることを特徴とする油圧回路。 - 前記第一フィルタは、前記オイルポンプから前記第二回路部に圧油を供給する油路から分岐して前記蓄圧部に圧油を供給する他の油路の途中に設けられていることを特徴とする請求項1に記載の油圧回路。
- 前記制御バルブは、前記蓄圧部から前記アクチュエータに油圧を供給する前記油路を開閉する供給バルブと、前記アクチュエータから排圧する排出バルブとを含み、
これらの供給バルブと排出バルブとは、弁座に弁体を押し付けてポートを密閉するように構成されていることを特徴とする請求項1または2に記載の油圧回路。 - 前記アクチュエータは、油圧が供給され、もしくは油圧が排出されることにより変速比を変化させる自動変速機の油圧室を含むことを特徴とする請求項1ないし3のいずれかに記載の油圧回路。
- 前記蓄圧部は、前記第二回路部に供給される油圧より高い油圧を蓄えるように構成されていることを特徴とする請求項1ないし4のいずれかに記載の油圧回路。
- 前記アクチュエータは、油圧が供給されることによりベルトの巻掛け溝の幅を狭くしてベルトの巻掛け半径を増大させる変速比用油圧室と、油圧が供給されることにより前記ベルトを挟み付ける挟圧力を増大させる挟圧力用油圧室とを含み、
前記第二回路部は、前記オイルポンプが吐出した圧油を連続的に供給して潤滑を行う潤滑部を含む
ことを特徴とする請求項1ないし5のいずれかに記載の油圧回路。 - 前記オイルポンプが吸入する圧油もしくは前記オイルポンプが吐出した圧油を通過させて異物を除去する第二フィルタを更に備え、
前記第一フィルタの目の粗さが、前記第二フィルタの目より細かいことを特徴とする請求項1ないし6のいずれかに記載の油圧回路。 - 前記オイルポンプから前記蓄圧部に圧油を供給する前記油路の途中に設けられ、かつ前記油路を連通状態と遮断状態とに切り替える第一開閉バルブを更に備えていることを特徴とする請求項1ないし7のいずれかに記載の油圧回路。
- 前記第一開閉バルブは、前記油路を連通させる状態と遮断する状態と前記蓄圧部をドレイン箇所に連通させた排圧状態とに選択的に切り替える切替バルブを含むことを特徴とする請求項8に記載の油圧回路。
- 前記オイルポンプから前記蓄圧部に圧油を供給する前記油路の途中に設けられた前記第一フィルタをバイパスするバイパス油路と、該バイパス油路を開閉する第二開閉バルブを更に備えていることを特徴とする請求項1ないし9のいずれかに記載の油圧回路。
- 前記第一フィルタで捕捉された異物を前記第一フィルタから離脱させる異物除去手段を更に備えていることを特徴とする請求項1ないし10のいずれかに記載の油圧回路の制御装置。
- 前記異物除去手段は、前記第一フィルタに対して前記蓄圧部側から前記第二回路側に圧油を流す手段を含むことを特徴とする請求項11に記載の油圧回路の制御装置。
- 前記蓄圧部の油圧が前記オイルポンプの吐出圧もしくは前記第二回路側の油圧より高圧の場合に前記油路が連通状態となるように前記第一開閉バルブを切り替えて前記第一フィルタで捕捉した異物を前記第一フィルタから離脱させる異物除去手段を備えていることを特徴とする請求項8ないし10のいずれかに記載の油圧回路の制御装置。
- 前記蓄圧部を前記ドレイン箇所に連通させるように前記切替バルブを切り替えて前記第一フィルタで捕捉した異物を前記第一フィルタから離脱させる異物除去手段を備えていることを特徴とする請求項9または10に記載の油圧回路の制御装置。
- 前記異物除去手段は、予め定めた一定の時間ごとに前記第一フィルタから異物を離脱させるように動作する手段を含むことを特徴とする請求項11ないし14のいずれかに記載の油圧回路の制御装置。
- 前記オイルポンプから前記蓄圧部に圧油を供給する前記油路の途中に設けられ、かつ前記油路を連通状態と遮断状態とに切り替える第一開閉バルブと、
前記蓄圧部の油圧が前記オイルポンプの吐出圧もしくは前記第二回路側の油圧より高圧でかつ前記挟圧力が予め定めた圧力以上の場合に前記油路が連通状態となるように前記第一開閉バルブを切り替えて前記第一フィルタで捕捉した異物を前記第一フィルタから離脱させる異物除去手段と
を更に備えていることを特徴とする請求項6に記載の油圧回路の制御装置。 - 前記オイルポンプから前記蓄圧部に圧油を供給する前記油路の途中に設けられ、かつ前記油路を連通させる状態と遮断する状態とドレイン箇所に連通させる状態とに切り替える切替バルブと、
前記挟圧力が予め定めた圧力以上の場合に前記蓄圧部を前記ドレイン箇所に連通させるように前記切替バルブを切り替えて前記第一フィルタで捕捉した異物を前記第一フィルタから離脱させる異物除去手段と
を更に備えていることを特徴とする請求項6に記載の油圧回路の制御装置。
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- 2011-02-14 US US13/983,817 patent/US9422951B2/en not_active Expired - Fee Related
- 2011-02-14 JP JP2012557684A patent/JP5644871B2/ja not_active Expired - Fee Related
- 2011-02-14 WO PCT/JP2011/053051 patent/WO2012111074A1/ja active Application Filing
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Cited By (3)
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---|---|---|---|---|
JP2014043877A (ja) * | 2012-08-24 | 2014-03-13 | Honda Motor Co Ltd | 油圧供給装置 |
JP2014101981A (ja) * | 2012-11-22 | 2014-06-05 | Bosch Corp | 変速機制御装置 |
CN111336248A (zh) * | 2020-04-07 | 2020-06-26 | 中国北方车辆研究所 | Amt执行机构液压供油系统故障诊断方法 |
Also Published As
Publication number | Publication date |
---|---|
US20130305701A1 (en) | 2013-11-21 |
JPWO2012111074A1 (ja) | 2014-07-03 |
JP5644871B2 (ja) | 2014-12-24 |
US9422951B2 (en) | 2016-08-23 |
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