WO2012060117A1 - Oil pressure control device provided with accumulator - Google Patents
Oil pressure control device provided with accumulator Download PDFInfo
- Publication number
- WO2012060117A1 WO2012060117A1 PCT/JP2011/056159 JP2011056159W WO2012060117A1 WO 2012060117 A1 WO2012060117 A1 WO 2012060117A1 JP 2011056159 W JP2011056159 W JP 2011056159W WO 2012060117 A1 WO2012060117 A1 WO 2012060117A1
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- WIPO (PCT)
- Prior art keywords
- pressure
- hydraulic
- oil
- accumulator
- supplied
- Prior art date
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- 238000005461 lubrication Methods 0.000 claims abstract description 51
- 238000001816 cooling Methods 0.000 claims abstract description 13
- 239000003921 oil Substances 0.000 claims description 287
- 230000001105 regulatory effect Effects 0.000 claims description 43
- 230000033228 biological regulation Effects 0.000 claims description 16
- 230000001276 controlling effect Effects 0.000 claims description 7
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- 238000010168 coupling process Methods 0.000 claims description 5
- 238000005859 coupling reaction Methods 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 4
- 239000010720 hydraulic oil Substances 0.000 claims description 3
- 238000007599 discharging Methods 0.000 claims 1
- 238000009825 accumulation Methods 0.000 abstract description 15
- 230000005540 biological transmission Effects 0.000 description 28
- 230000001050 lubricating effect Effects 0.000 description 18
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Images
Classifications
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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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
- F16H61/0025—Supply of control fluid; Pumps therefore
-
- 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
- F16H61/0025—Supply of control fluid; Pumps therefore
- F16H61/0031—Supply of control fluid; Pumps therefore using auxiliary pumps, e.g. pump driven by a different power source than the engine
-
- 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
-
- 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
- F16H2061/0037—Generation or control of line pressure characterised by controlled fluid supply to lubrication circuits of the gearing
Definitions
- the present invention relates to a hydraulic control device configured to supply hydraulic pressure generated by a hydraulic pump to various actuators, a lubrication unit, and the like and store the hydraulic pressure in an accumulator.
- the devices described in these patent documents are for controlling a transmission mounted on a vehicle, and the device described in Japanese Patent Application Laid-Open No. 2004-84928 is a hydraulic pump driven by a motor.
- a selection valve is connected to the discharge port, and hydraulic pressure is selectively supplied from the selection valve to the accumulator and the lubrication circuit.
- the device described in International Publication No. 2010/021218 is configured for a continuously variable transmission, and a continuously variable transmission, a starting clutch, and the like are used as a high pressure portion, and torque is applied to the continuously variable transmission.
- the converter and various lubricating parts are low pressure parts, and the hydraulic pressure generated by the hydraulic pump is supplied in parallel to the high pressure part and the low pressure part.
- the high pressure section is provided with an accumulator that stores the hydraulic pressure required for the continuously variable transmission and the forward clutch.
- the accumulator hydraulic pressure causes the continuously variable transmission and
- a transmission mechanism such as a clutch is configured to maintain a predetermined transmission torque capacity.
- the supply of pressure oil to the actuator, the lubrication unit or the cooling unit and the pressure accumulation to the accumulator are usually performed by a single hydraulic pump.
- the selection valve is configured to switch between supply of hydraulic pressure to the lubrication circuit and accumulation of pressure, while the accumulation of pressure is being performed, the lubrication unit and the cooling unit are connected.
- the supply of pressure oil may be interrupted, resulting in lack of lubrication or cooling.
- a high-pressure part including an accumulator and a low-pressure part such as a lubricating part are connected in parallel to the hydraulic pump, Therefore, when the pressure oil is stored in the accumulator with a high pressure, the amount of oil supplied from the pressure regulating valve to the lubrication point is reduced.
- the hydraulic pumps of hydraulic control devices mounted on vehicles are often so-called mechanical pumps (mechanical pumps) driven by an engine, and the discharge amount does not change greatly with such mechanical pumps. There may be a shortage.
- This invention was made paying attention to said technical subject, and it aims at providing the hydraulic control apparatus which can prevent or suppress insufficient lubrication, insufficient cooling, etc. even at the time of pressure accumulation. It is.
- the present invention provides a hydraulic pump, a pressure accumulator that stores the hydraulic pressure discharged from the hydraulic pump, the accumulator connected in parallel to the hydraulic pump, and the hydraulic pump A hydraulic regular portion that always requires hydraulic pressure when operating, and the hydraulic regular portion is generated by regulating the hydraulic pressure discharged from the hydraulic pump to the pressure supplied to the accumulator side.
- the pressure oil adding means includes a high pressure side oil passage that guides the oil pressure discharged from the hydraulic pump to the pressure accumulator, and an oil amount supplied to the hydraulic regular portion by being driven by the oil pressure of the high pressure side oil passage. It can be configured by an oil amount amplifying unit that increases.
- the control device may further include a normal oil passage that guides the pressure oil that is generated by adjusting pressure to the hydraulic normal portion, and a bypass oil passage that communicates the high-pressure side oil passage with the normal oil passage.
- the oil amount amplifying unit is provided in the middle of the bypass oil passage, and is configured by a jet pump that pumps oil from the storage portion with a negative pressure generated when the pressure oil flowing through the bypass oil passage is injected. can do.
- the hydraulic control device further includes a blocking mechanism that blocks the flow of pressure oil to the oil amount amplifying unit when hydraulic pressure is not supplied from the hydraulic pump to the accumulator via the high pressure side oil passage. Further, it can be provided.
- the shut-off mechanism is opened when pressure oil is provided to the hydraulic pump side of the high-pressure side oil passage at a location closer to the hydraulic pump than the location where the bypass oil passage is branched.
- a first on-off valve that is provided between the discharge part of the oil amount amplifying part and the normal oil path in the bypass oil path, and is opened when pressure oil is directed toward the normal oil path.
- the structure may include two on-off valves.
- the first on-off valve is opened when the valve opening force required for valve opening is set to a predetermined value by an elastic force, and the pressure of the pressure oil directed toward the accumulator exceeds the valve opening force, and the accumulator is opened. It can be configured by a check valve that closes and blocks the flow of pressure oil in the direction opposite to the directed direction.
- the second on-off valve can be constituted by a check valve that is opened by pressure oil directed toward the regular oil passage.
- the hydraulic control device of the present invention may further include an engine that drives the hydraulic pump, and an electric hydraulic pump that is driven by a motor and discharges pressure oil.
- an engine that drives the hydraulic pump
- an electric hydraulic pump that is driven by a motor and discharges pressure oil.
- hydraulic pressure When hydraulic pressure is supplied from the hydraulic pump to the pressure accumulator, it may be configured by a switching valve that switches so as to supply pressure oil discharged from the electric hydraulic pump to the hydraulic pressure regular part.
- the switching valve communicates the electric hydraulic pump with the hydraulic service portion by adjusting the hydraulic pressure discharged from the hydraulic pump to the pressure supplied to the accumulator side, and the hydraulic pressure discharged from the hydraulic pump is reduced. It may be a valve that switches so that the electric hydraulic pump communicates with the pressure accumulator side by being regulated to a pressure lower than the pressure supplied to the pressure accumulator side.
- the present invention provides an insufficient amount of hydraulic oil supplied from the hydraulic pump to the hydraulic service portion when supplying the hydraulic oil discharged from the hydraulic pump to the accumulator side.
- an electric hydraulic pump control means for controlling the electric hydraulic pump based on the shortage amount of the pressure oil calculated by the shortage amount calculating means.
- the electric hydraulic pump includes an oil pump that discharges pressure oil according to the number of rotations, and the electric hydraulic pump control means discharges the deficient amount of the pressure oil calculated by the deficient amount calculating means. May include means for controlling the rotational speed of the electric hydraulic pump or the motor.
- the hydraulic control device of the present invention can further include a fluid coupling having a lock-up clutch that is engaged and released by hydraulic pressure, and a lock-up control valve that generates a hydraulic pressure that controls the lock-up clutch.
- the pressure oil adding means may include an oil amount amplifying unit that is driven by the pressure oil supplied to the lock-up clutch and increases the amount of oil supplied to the hydraulic regular portion.
- the oil amount amplifying unit is disposed between an oil passage that supplies hydraulic pressure to the lock-up clutch and an oil passage that supplies pressure oil to the hydraulic regular portion, and the pressure oil supplied toward the lock-up clutch It can be constituted by a jet pump that pumps up oil from the reservoir with a negative pressure generated by injecting a part of the oil.
- a switching valve that is closed to shut off the supply of pressure oil to the jet pump can be further provided.
- a pressure regulating valve that regulates the hydraulic pressure generated by the hydraulic pump can be further provided.
- the drain hydraulic pressure generated by the pressure regulation in the pressure regulating valve is supplied to the hydraulic regular portion. It may be constituted so that.
- the hydraulic service portion in each of the above-described configurations may include at least one of a lubrication location and a cooling location that is cooled by oil.
- the pressure control valve further adjusts the hydraulic pressure generated by the hydraulic pump and outputs a signal pressure in accordance with the pressure control level, and the drain hydraulic pressure generated by the pressure adjustment in the pressure control valve is the normal hydraulic pressure.
- the switching valve can be configured by a valve that is switched by the signal pressure.
- the hydraulic pressure supplied to the pressure accumulator is higher than the hydraulic pressure supplied to the hydraulic regular portion such as the lubrication portion, and the hydraulic pressure supplied to the pressure accumulator and the hydraulic regular portion is generated by the hydraulic pump. For this reason, when the pressure adjustment level is increased to accumulate pressure, the amount of hydraulic pressure generated due to pressure adjustment such as drain hydraulic pressure is reduced.
- the hydraulic pressure adding means operates to add pressure oil other than the pressure oil discharged by the hydraulic pump to the pressure oil supplied to the hydraulic pressure regular part. Therefore, according to the present invention, it is possible to avoid or suppress a shortage of the amount of pressure oil in the hydraulic regular portion during pressure accumulation.
- the hydraulic pressure adding means in the present invention is configured by a jet pump or the like that pumps oil from the reservoir by operating with a relatively high hydraulic pressure supplied to the pressure accumulator side or a hydraulic pressure supplied to the lockup clutch. It is composed of an oil-absorbing part. Therefore, it is not necessary to provide a new oil pressure generation source in order to increase the oil amount.
- the present invention is a hydraulic control device configured to avoid a shortage of pressure oil in the hydraulic regular portion when accumulating pressure, and therefore, when pressure accumulation is not performed, an increase in pressure oil relative to the hydraulic regular portion is increased.
- a blocking mechanism can be provided to prevent this. When configured in this way, excessive supply of pressure oil to the hydraulic regular portion is avoided or suppressed, so that power loss can be reduced.
- this invention can provide the electric hydraulic pump which generate
- the discharge amount according to the rotation speed of the electric hydraulic pump can be configured to be controlled based on the amount of oil that is insufficient in the hydraulic regular portion, and in this case, the hydraulic regular portion Therefore, the pressure oil can be supplied without excess or deficiency, and unnecessary driving of the electric hydraulic pump can be avoided or suppressed.
- insufficient lubrication and insufficient cooling during pressure accumulation can be avoided or suppressed in advance.
- FIG. 1 schematically shows an example in which the present invention is applied to a hydraulic control device intended for a continuously variable transmission mounted on a vehicle.
- the continuously variable transmission 1 is a belt type that is conventionally known, and a belt 4 is wound around a driving pulley 2 and a driven pulley 3 to transmit torque between the pulleys 2 and 3, and The gear ratio is changed by changing the wrapping radius of the belt around the pulleys 2 and 3.
- Each pulley 2 and 3 includes a fixed sheave and a movable sheave arranged so as to approach and separate from the fixed sheave, and a V-groove belt winding groove between the fixed sheave and the movable sheave. Is formed.
- the pulleys 2 and 3 are provided with hydraulic actuators 5 and 6 for moving the movable sheave back and forth in the direction of its axis.
- Either one of these hydraulic actuators 5, 6, for example, the hydraulic actuator 6 in the driven pulley 3, is supplied with a hydraulic pressure that generates a clamping pressure with which the pulleys 2, 3 clamp the belt 4.
- the other of the hydraulic actuators 6, for example, the hydraulic actuator 5 in the drive pulley 2 is supplied with hydraulic pressure for changing the belt wrapping radius.
- a C1 clutch 7 for transmitting / cutting drive torque is provided on the input side or output side of the continuously variable transmission 1.
- the C1 clutch 7 is a clutch in which the transmission torque capacity is set according to the supplied hydraulic pressure, and is constituted by, for example, a wet multi-plate clutch.
- the continuously variable transmission 1 and the C1 clutch 7 transmit torque for traveling of the vehicle, and are set to a transmission torque capacity corresponding to the hydraulic pressure. Therefore, the hydraulic actuators 5, 6 and C1
- the clutch 7 is supplied with a high hydraulic pressure corresponding to the torque to be transmitted. That is, the continuously variable transmission 1 or its hydraulic actuators 5 and 6 and the C1 clutch 7 or its hydraulic chamber (not shown) constitute a so-called high hydraulic pressure supply section.
- a torque converter (torque converter) 8 having a lockup clutch (not shown) is arranged in series with the continuously variable transmission 1.
- the torque converter 8 is the same as that conventionally known.
- a torque amplifying action occurs.
- the rotational speed difference is small, that is, in a coupling range in which these speed ratios are larger than a predetermined value, it is configured to function as a fluid coupling having no torque amplification action.
- the lockup clutch is configured to directly connect a front cover integrated with a pump impeller as an input side member and a hub integrated with a turbine runner via a friction plate.
- a lockup control valve 9 is provided for controlling the lockup hydraulic pressure for bringing the friction plate into contact with the front cover and separating the friction plate.
- the lock-up control valve 9 is for controlling the direction and pressure of the hydraulic pressure supplied to the lock-up clutch, and therefore the lock-up control valve 9 operates at a relatively low hydraulic pressure.
- the power transmission device including the continuously variable transmission 1 and the torque converter 8 described above has many so-called sliding portions or heat generating portions such as bearings and bearings that are in frictional contact with each other.
- the lubrication unit 10 only needs to be supplied with a required amount of lubricating oil even at a low pressure, the lubrication unit 10, the lock-up control valve 9, or the torque converter 8 is a so-called low hydraulic pressure supply unit. .
- a mechanical hydraulic pump 12 driven by an engine 11 mounted on a vehicle is provided.
- the mechanical hydraulic pump 12 is configured to be able to supply hydraulic pressure to the high hydraulic pressure supply unit and the low hydraulic pressure supply unit described above.
- a pressure regulating valve 13 for regulating the hydraulic pressure discharged from the mechanical hydraulic pump 12 to a predetermined pressure is provided.
- This pressure regulating valve 13 is for regulating the hydraulic pressure discharged from the mechanical hydraulic pump 12 to a relatively low pressure, and is required, for example, at the supply port of the lockup control valve 9 for the lockup clutch described above. It is configured so as to regulate the hydraulic pressure.
- the pressure regulating valve 13 is configured to discharge a part of the supplied pressure oil and set it to the target pressure, the pressure oil is discharged along with the pressure adjustment.
- the discharge hydraulic pressure (drain hydraulic pressure) is supplied to the lubrication unit 10 through the oil passage 14.
- the lubrication portion 10 corresponds to the hydraulic regular portion in the present invention
- the oil passage 14 corresponds to the regular oil passage in the present invention.
- an alternator 15 that is driven by the engine 11 to generate electric power is provided.
- This alternator 15 is the same as that mounted on a vehicle that uses an internal combustion engine as a power source, and is configured to charge the generated power to a battery (not shown) and to supply various electrical equipment.
- the motor 17 of the electric hydraulic pump 16 is supplied with power and driven.
- the electric hydraulic pump 16 is mainly for supplying hydraulic pressure to a high hydraulic pressure supply unit, and an accumulator (pressure accumulator) 20 is connected to an oil passage 18 connected to the discharge port via a check valve 19. Is connected.
- the check valve 19 is configured to close so that the pressure oil does not flow backward from the accumulator 20 toward the electric hydraulic pump 16 when the discharge pressure of the electric hydraulic pump 16 is lower than the hydraulic pressure of the accumulator 20. ing.
- the oil passage 18 communicates with the actuator 5 in the driving pulley 2, the actuator 6 in the driven pulley 3, and the C1 clutch 7 in order to supply the hydraulic pressure of the electric hydraulic pump 16 or the accumulator 20 to the above-described high hydraulic pressure supply unit.
- the hydraulic pressure of the actuators 5 and 6 and the C1 clutch 7 is controlled by an electromagnetic valve that is electrically controlled to open and close the oil passage.
- a supply electromagnetic valve DSP1 is provided, and an exhaust pressure electromagnetic valve DSP2 is connected to the actuator 5.
- the supply solenoid valve DSP1 hydraulic pressure is supplied to the actuator 5 in the drive pulley 2 to narrow (upshift) the belt groove of the drive pulley 2, and by opening the exhaust pressure solenoid valve DSP2, the drive pulley
- the pressure oil is discharged from the actuator 5 in 2 to an atmosphere opening part such as an oil storage part to widen (downshift) the belt groove of the drive pulley 2.
- the speed ratio control by the electromagnetic valves DSP1 and DSP2 can be performed by feedback control or feedback / feedforward control based on a deviation between the target speed ratio and the actual speed ratio.
- Such control of supply / discharge of hydraulic pressure is performed similarly for the actuator 6 and the C1 clutch 7 in the driven pulley 3. That is, a supply electromagnetic valve DSS1 is provided in an oil passage for supplying hydraulic pressure from the oil passage 18 to the actuator 6 in the driven pulley 3, and an exhaust pressure electromagnetic valve DSS2 is connected to the actuator 6. That is, by opening the supply electromagnetic valve DSS1, the hydraulic pressure is supplied to the actuator 6 in the driven pulley 3 to increase the pressure (clamping pressure) for pinching the belt 4 by the driven pulley 3, and the exhaust pressure electromagnetic valve DSS2 is opened. Thus, the hydraulic pressure is discharged from the actuator 6 in the driven pulley 3 to an air release part such as an oil storage part to reduce the clamping pressure.
- the clamping pressure can be controlled by feed-forward control or feedback / feed-forward control based on a required drive amount such as the accelerator opening.
- a supply electromagnetic valve DSC1 is provided in an oil passage for supplying hydraulic pressure from the oil passage 18 to the C1 clutch 7, and an exhaust pressure electromagnetic valve DSC2 is connected to the C1 clutch 7. That is, by opening the supply electromagnetic valve DSC1, the hydraulic pressure is supplied to the C1 clutch 7 and engaged therewith, and by opening the exhaust pressure electromagnetic valve DSC2, the hydraulic pressure is discharged from the C1 clutch 7 and released. It is configured.
- the oil passage 21 corresponds to the high-pressure side oil passage in the present invention, and a check valve 22 for preventing the backflow of pressure oil from the accumulator 20 toward the mechanical hydraulic pump 12 is provided in the middle thereof. It has been.
- pressure oil is supplied to the portion of the oil passage 21 upstream of the check valve 22 and the location of the hydraulic pressure regulated by the pressure regulating valve 13 such as the discharge port of the mechanical hydraulic pump 12 and the lubricating portion 10 described above.
- An oil passage 23 is provided for communicating with the oil passage 14 to be communicated.
- the oil passage 23 corresponds to a bypass oil passage in the present invention, and is hereinafter referred to as a bypass oil passage 23.
- An oil amount amplifying unit 24 that pumps up oil using the pressure oil flowing through the bypass oil passage 23 and increases the supply amount of the pressure oil to the lubrication unit 10 with the oil is provided in the middle of the bypass oil passage 23. . Further, a pressure reducing orifice 25 is provided on the inflow side (upstream side in the flow direction of the pressure oil) of the oil amount amplifying unit 24.
- the oil amount amplifying unit 24 only needs to have a pump function that pumps oil from the storage unit 26 such as an oil pan by the energy of the pressure oil flowing through the bypass oil passage 23 and supplies the oil to the lubricating unit 10.
- the oil amount amplifying unit 24 can be configured by a jet pump (or an ejector pump).
- the jet pump has a known structure that includes a nozzle 27 that squeezes the pressure oil flowing through the bypass oil passage 23 to increase its flow velocity, and a diffuser 28 that has a discharge side that expands in a tapered shape and into which a jet of pressure oil is blown from the nozzle 27.
- a negative pressure is generated at the inlet portion of the diffuser 28.
- the negative pressure causes the oil to be pumped up from the storage portion 26, mixed with the pressure oil injected from the nozzle 27, and supplied to the lubricating portion 10. Therefore, the pressure oil supplied to the lubrication unit 10 is increased by the amount pumped up from the storage unit 26.
- the transmission torque capacity of the continuously variable transmission that is, the belt clamping pressure
- the hydraulic pressure required to set the transmission torque capacity and the gear ratio is required.
- the hydraulic pressure is mainly generated by the electric hydraulic pump 16 or supplied from the accumulator 20.
- the relatively high hydraulic pressure is supplied to the continuously variable transmission 1 and the C1 clutch 7 via the oil passage 18.
- the hydraulic pressures in the actuators 5 and 6 and the C1 clutch 7 are electrically opened and closed by the supply solenoid valves DSP1, DSS1, DSC1 and the exhaust solenoid valves DSP2, DSS2, DSC2, as described above. Be controlled. Further, if the engine 11 is driven, transmission members such as the torque converter 8 and other gears are rotating. Therefore, the torque converter 8 and various lubrication units are driven from the mechanical hydraulic pump 12 driven by the engine 11. 10 is supplied with pressurized oil. Specifically, the hydraulic pressure generated by the mechanical hydraulic pump 12 is regulated to a predetermined pressure by the pressure regulating valve 13, and the hydraulic pressure is supplied to the torque converter 8 via the lockup control valve 9 described above to lock up. Engagement / release control of the clutch is executed. Further, the drain hydraulic pressure generated by the pressure adjustment is supplied to the lubrication unit 10 through the oil passage 14 and is used for lubrication of the bearings, the tooth surfaces of the gears, and the like.
- part of the pressure oil discharged from the mechanical hydraulic pump 12 flows into the bypass oil passage 23 via the high-pressure side oil passage 21. Since the pressure oil in the bypass oil passage 23 is injected from the nozzle 27 in the oil amount amplifying unit 24 to generate a negative pressure, the oil in the storage portion 26 is pumped up here and lubricated together with the pressure oil in the bypass oil passage 23. Supplied to the unit 10. That is, the amount of pressure oil for the lubrication part 10 is increased.
- a cooling unit that needs to be cooled by oil can be connected in parallel with the lubrication unit 10, and these lubrication unit 10 and the cooling unit are in a state where the engine 11 that drives the mechanical hydraulic pump 12 is operating.
- the mechanical hydraulic pump 12 is generating hydraulic pressure, the amount of pressure oil is not limited to the amount discharged from the mechanical hydraulic pump 12, and the reservoir 26 Therefore, the shortage of the lubricating oil amount and the cooling oil amount is surely avoided or suppressed.
- the amount of pressure oil with respect to the lubrication part 10 may be increased using the oil_pressure
- FIG. 1 since the hydraulic pressure is supplied to the high-pressure side oil passage 21 even when accumulator 20 is not accumulating, the amount of pressure oil is increased with respect to the lubrication unit 10 regardless of whether or not accumulating is performed. It will be.
- the oil amount amplifying unit 24 is originally provided to increase the amount of pressure oil to the lubricating unit 10 when accumulating the accumulator 20, the oil amount amplifying unit 24 is configured to operate only when accumulating pressure. It is preferable to do. An example is shown in FIG.
- shut-off mechanism that shuts off the pressure oil to the oil amount amplifying unit 24 is provided.
- the shut-off mechanism shown in FIG. 2 includes a valve that shuts off the pressure oil from the mechanical hydraulic pump 12 to the oil amount amplifying unit 24, and a valve that shuts off the pressure oil that flows back from the lubrication unit 10 to the oil amount amplifying unit 24. Has been.
- valves may be an on-off valve that can be controlled electrically or an on-off valve that can be controlled by hydraulic pressure, but in the example shown in FIG. That is, the pressure (opening pressure) for opening the valve to the mechanical hydraulic pump 12 side rather than the check valve 22 for preventing the backflow of the pressure oil from the accumulator 20 or the oil passage 18 in the high-pressure side oil passage 21 is an elastic force.
- the pressure accumulation check valve 29 set in (1) is provided.
- the valve opening force is a force corresponding to the minimum pressure of the hydraulic pressure stored in the accumulator 20, and is therefore closed when the hydraulic pressure generated by the mechanical hydraulic pump 12 is not stored in the accumulator 20.
- the aforementioned bypass oil passage 23 branches from the high-pressure side oil passage 21 between the pressure accumulation check valve 29 and the check valve 22 provided adjacent thereto. Therefore, when the hydraulic pressure generated by the mechanical hydraulic pump 12 is not accumulated in the accumulator 20, the pressure oil is not supplied to the bypass oil passage 23.
- a check valve 30 is provided on the discharge side of the oil amount amplifying unit 24.
- the check valve 30 opens when the discharge pressure of the oil amount amplifying unit 24 is higher than the oil pressure of the oil passage 14 that supplies the pressure oil from the pressure regulating valve 13 to the lubricating unit 10. Is a valve configured to close in the opposite case. Therefore, when the oil amount amplifying unit 24 is not operating and the discharge pressure is relatively low, the lubricating unit 10 or pressurized oil is supplied to the lubricating unit 10. The pressure oil is configured not to flow backward from the oil passage 14 to be supplied to the oil amount amplifying unit 24.
- the hydraulic pressure supplied to the accumulator 20 side is used as a source pressure for operating the jet pump constituting the oil amount amplifying unit 24, and the hydraulic pressure is supplied to the jet pump via the bypass oil passage 23.
- other hydraulic pressure can be used as the driving hydraulic pressure of the jet pump.
- FIG. 3 An example is shown in FIG.
- the example shown in FIG. 3 is a hydraulic control apparatus in which a part of the configuration shown in FIG. 2 is changed. Therefore, the same parts as those shown in FIG. A description of the configuration different from the configuration shown in FIG.
- An inflow port of the jet pump (that is, an inflow port of the nozzle 27) constituting the oil amount amplifying unit 24 and an oil passage 31 for supplying the hydraulic pressure regulated by the lockup control valve 9 to the torque converter 8 are communicated with each other.
- a bypass oil passage 32 is provided.
- the bypass oil passage 32 is provided with a switching valve 33 that is switched between an open state and a closed state by a signal pressure.
- the pressure regulation valve 13 in the example shown in FIG. 3 is configured to output a signal pressure in accordance with (or based on) the pressure regulation level, and more specifically, the accumulator 20 side for pressure accumulation. When the pressure adjustment level is increased so as to supply the hydraulic pressure, a signal pressure based on the pressure adjustment level is output.
- the switching valve 33 is, for example, a spool type valve, and is configured to act by opposing the signal pressure and the elastic force of the spring across the spool.
- the elastic force of the spring is set to be smaller than the thrust generated based on the signal pressure. Therefore, when the signal pressure is applied, the spool moves by compressing the spring, and as a result, the spring is opened and locked up.
- the control oil pressure of the clutch is supplied to the jet pump and the signal pressure does not act on the contrary, the spool is pushed by the spring to be closed, and as a result, the lockup control oil pressure for the jet pump is shut off. .
- the pressure regulation level of the pressure regulating valve 28 increases, and the pressure regulation is accompanied accordingly.
- the amount of drain hydraulic pressure generated in the valve 28, that is, the amount of pressure oil sent to the lubricating portion 10 is reduced.
- the pressure regulating valve 28 outputs a signal pressure as the pressure regulating level increases, and this is supplied to the switching valve 33, so that the switching valve 33 is switched to the open state.
- the lock-up control hydraulic pressure is sent to the jet pump via the switching valve 33 and injected from the nozzle 27 toward the diffuser 28, and oil is pumped up from the reservoir 26 such as an oil pan by the negative pressure generated accordingly. Then, the oil pushes the check valve 30 open and is supplied to the lubrication unit 10. That is, the amount of pressure oil supplied to the lubrication unit 10 is increased.
- the mechanical hydraulic pump 12 driven by the engine 11 can generate a high pressure required in the continuously variable transmission 1 and the like, and can accumulate the pressure. At the same time, even if the pressure is low, the pressure oil can be supplied without excess or deficiency to the hydraulic regular part such as the lubrication part 10 that needs to supply the pressure oil continuously.
- FIG. 4 shows such an example, in which the oil in the reservoir 26 is pumped up and supplied to the lubricating unit 10 by the electric hydraulic pump 16 instead of the jet pump described above.
- a switching valve 34 for switching a hydraulic pressure supply point is communicated with the discharge side of the electric hydraulic pump 16.
- the switching valve 34 includes an input port connected to the electric hydraulic pump 16, an output port connected to the accumulator 20 and the high hydraulic pressure supply unit via the check valve 19, and a lubrication unit via a bypass oil passage 35. And an output port communicated with the input port according to the presence or absence of signal pressure.
- the switching valve 34 is a spool-type valve, and is configured to act by opposing the signal pressure and the elastic force of the spring across the spool.
- the elastic force of the spring is set to be smaller than the thrust generated based on the signal pressure. Therefore, when the signal pressure acts, the spool moves by compressing the spring, and as a result, the electric hydraulic pump 16 is bypassed by the bypass oil. In contrast, when the signal pressure does not act, the spool is pushed by a spring so that the electric hydraulic pump 16 communicates with the accumulator 20 side.
- the pressure regulating valve 28 is configured to output a signal pressure, and the signal pressure is supplied to the switching valve 34. Specifically, when the pressure regulation level is increased to accumulate pressure in the accumulator 20, a signal pressure is output from the pressure regulating valve 28, and the switching valve 34 is switched by the signal pressure to cause the electric hydraulic pump 16 to bypass the oil passage. It is configured to communicate with the lubrication unit 10 via 35. Since the other configuration is the same as the configuration shown in any of FIGS. 1 to 3, the same reference numerals are given to the same parts as those shown in these drawings, and the description thereof is omitted.
- the electric hydraulic pump 16 is configured such that the discharge amount or the discharge pressure increases according to the rotation speed or the rotation speed of the motor 17.
- the required hydraulic pressure is determined in advance, so that the rotational speed of the electric hydraulic pump 16 or the motor 17 depends on the accumulator 20 or the high hydraulic pressure supply. It is set to generate the hydraulic pressure required by the section.
- the hydraulic pressure required by the hydraulic service section such as the lubrication section 10 is lower than the hydraulic pressure stored in the accumulator 20, and the electric hydraulic pump 16 discharges to increase the pressure oil supplied to the lubrication section 10.
- the amount of oil to do may be small. Therefore, when auxiliary pressure oil is supplied to the lubrication unit 10, the electric hydraulic pump 16 or the motor 17 is controlled differently from the normal case of supplying hydraulic pressure to the accumulator 20 or the high hydraulic pressure supply unit. .
- FIG. 5 is a flowchart for explaining an example of the control. Whether or not the command pressure Psol for the control solenoid (SOL) of the pressure regulating valve 28 is higher than the minimum signal pressure Pacc_min of the control solenoid when accumulating in the accumulator 20. Is determined (step S1). This determination is made as to whether or not the hydraulic pressure discharged from the mechanical hydraulic pump 12 driven by the engine 11 is adjusted to a high pressure so as to be accumulated in the accumulator 20, or whether or not the accumulator 20 is accumulated. If the determination in step S1 is negative, there is no need to increase the amount of pressure oil to the lubrication unit 10, so the routine proceeds to a routine for performing normal control (step S2) of the electric hydraulic pump 16. . On the other hand, if the command pressure to the pressure regulating valve 28 is high so as to accumulate pressure in the accumulator 20 and the determination is affirmative in step S1, an insufficient flow rate Qlub is calculated (step S3).
- the calculation can be performed based on the engine (Eng speed) and the accumulated pressure. That is, since the mechanical hydraulic pump 12 is driven by the engine 11, the discharge amount of the mechanical hydraulic pump 12 can be obtained based on the engine speed, and the amount of pressure oil supplied to the accumulator 20 is the accumulated pressure. The difference between these flow rates is the amount of oil supplied to the lubrication unit 10 and the torque converter 8, and the amount of oil required by the lubrication unit 10 is determined in advance. The deficiency can be determined based on the amount of oil.
- step S4 Based on the insufficient lubrication flow rate Qlub thus calculated, the rotational speed of the electric hydraulic pump 16 is calculated (step S4). Since the discharge amount per rotation of the electric hydraulic pump 16 is determined by design as a so-called pump specification, the required number of rotations is obtained based on the insufficient lubrication flow rate Qlub. A drive command for the motor 17 is output so as to obtain the rotation speed thus obtained (step S5).
- the electric hydraulic pump 16 is controlled according to normal control, and the accumulator 20 and the high hydraulic pressure supply unit are controlled. As long as the hydraulic pressure is not required, it is maintained in a stopped state. In other words, the electric hydraulic pump 16 or the motor 17 is not driven unnecessarily, and power is not consumed accordingly.
- the pressure regulation level of the pressure regulating valve 28 increases, and the pressure regulation is accompanied accordingly.
- the amount of drain hydraulic pressure generated in the valve 28, that is, the amount of pressure oil sent to the lubricating portion 10 is reduced.
- the pressure regulating valve 28 outputs a signal pressure as the pressure regulating level increases, and this is supplied to the switching valve 34. Therefore, the operating state of the switching valve 34 is switched, and the electric hydraulic pump 16 communicates with the lubrication unit 10 via the bypass oil passage 35.
- step S1 shown in FIG. 5 the command pressure for the pressure regulating valve 28 is increased, so that an affirmative determination is made in step S1 shown in FIG. 5.
- the electric hydraulic pump 16 discharges an insufficient amount of pressure oil in the lubrication unit 10.
- the pressure oil discharged in this way is supplied to the lubrication unit 10 via the bypass oil passage 35. That is, the amount of pressure oil supplied to the lubrication unit 10 is increased, and the shortage is avoided or suppressed.
- the above-described jet pump, electric hydraulic pump 16 or ipass oil passages 23, 32, and 35 correspond to pressure oil adding means in the present invention. Further, the jet pump and the electric hydraulic pump 16 correspond to the oil amount amplifying unit in the present invention. Further, the pressure accumulation check valve 29 and the check valve 30 shown in FIG. 2 correspond to the shut-off mechanism or the first and second on-off valves in the present invention. Furthermore, the electronic control device having the function of executing step S3 shown in FIG. 5 and the function of executing steps S4 and S5 corresponds to the deficient amount calculating means and the electric hydraulic pump control means in the present invention.
- the control device for continuously variable transmission 1 has been described as an example.
- the present invention is not limited to the above-described specific example, and a hydraulic control device for other types of transmissions.
- the hydraulic control device can be applied to a hydraulic control device for devices other than the transmission and the transmission, and in short, the hydraulic control device is configured to branch and supply the hydraulic pressure from one hydraulic pump to the accumulator and the hydraulic service unit Can be applied to.
- the oil amount amplifying part in the present invention may be a pump other than the jet pump, the ejector pump or the electric hydraulic pump described above. In short, when the pressure is accumulated in the accumulator, the pressure oil for the hydraulic regular part such as a lubricating part is used.
- the hydraulic regular part in this invention may be an appropriate cooling part that cools by continuously supplying pressure oil, in addition to the above-described lubricating part. And in this invention, it replaced with the torque converter and the fluid coupling provided with the lockup clutch may be provided.
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Abstract
Description
Claims (17)
- 油圧ポンプと、その油圧ポンプが吐出した油圧を蓄える蓄圧器と、前記油圧ポンプに対して前記蓄圧器とは並列に接続されかつ前記油圧ポンプが動作しているときに油圧を常時必要とする油圧常用部とを備え、その油圧常用部には前記油圧ポンプから吐出された油圧を前記蓄圧器側に供給する圧力に調圧することに伴って生じた圧油が供給され、前記蓄圧器には前記油圧常用部で必要とする圧力より高い油圧が蓄えられるように構成された、蓄圧器を備えた油圧制御装置において、
前記油圧ポンプが吐出した油圧が前記蓄圧器に供給される場合に、前記調圧に伴って生じた圧油以外の圧油を前記油圧常用部に供給する圧油追加手段を備えていることを特徴とする、蓄圧器を備えた油圧制御装置。 A hydraulic pump, a pressure accumulator for storing the hydraulic pressure discharged from the hydraulic pump, and a hydraulic pressure that always requires hydraulic pressure when the pressure accumulator is connected in parallel to the hydraulic pump and the hydraulic pump is operating A hydraulic unit, and the hydraulic unit is supplied with pressure oil generated by adjusting the hydraulic pressure discharged from the hydraulic pump to a pressure to be supplied to the accumulator side. In a hydraulic control device having a pressure accumulator configured to store a higher hydraulic pressure than the pressure required in the hydraulic regular part,
When the hydraulic pressure discharged from the hydraulic pump is supplied to the accumulator, pressure oil adding means is provided for supplying pressure oil other than the pressure oil generated with the pressure adjustment to the hydraulic pressure regular part. A hydraulic control device including a pressure accumulator. - 前記圧油追加手段は、前記油圧ポンプが吐出した油圧を前記蓄圧器に導く高圧側油路と、その高圧側油路の油圧によって駆動されることにより前記油圧常用部に供給される油量を増大させる油量増幅部とを備えていることを特徴とする請求項1に記載の蓄圧器を備えた油圧制御装置。 The pressure oil adding means is configured to control a hydraulic pressure discharged from the hydraulic pump to the pressure accumulator and an oil amount supplied to the hydraulic pressure normal portion by being driven by a hydraulic pressure of the high pressure side oil path. The oil pressure control device provided with the pressure accumulator according to claim 1, further comprising an oil amount amplifying unit to be increased.
- 調圧されて生じる圧油を前記油圧常用部に導く常用油路と、前記高圧側油路と常用油路とを連通させるバイパス油路とを更に備え、
前記油量増幅部は、前記バイパス油路の途中に設けられ、前記バイパス油路を流れる圧油を噴射させることに伴って生じる負圧でオイルを貯留部から汲み上げるジェットポンプを含むことを特徴とする請求項2に記載の蓄圧器を備えた油圧制御装置。 A normal oil passage that guides the pressure oil generated by pressure regulation to the hydraulic normal portion; and a bypass oil passage that connects the high-pressure side oil passage and the normal oil passage;
The oil amount amplifying unit includes a jet pump that is provided in the middle of the bypass oil passage and pumps up the oil from the storage portion with a negative pressure generated by injecting the pressure oil flowing through the bypass oil passage. A hydraulic control apparatus comprising the pressure accumulator according to claim 2. - 前記油圧ポンプから前記高圧側油路を介して前記蓄圧器に油圧を送給しない場合に前記油量増幅部への圧油の流れを遮断する遮断機構が更に設けられていることを特徴とする請求項2または3に記載の蓄圧器を備えた油圧制御装置。 When the hydraulic pressure is not supplied from the hydraulic pump to the accumulator via the high-pressure side oil passage, a shut-off mechanism for shutting off the flow of the pressure oil to the oil amount amplifying unit is further provided. A hydraulic control apparatus comprising the pressure accumulator according to claim 2.
- 前記遮断機構は、前記高圧側油路のうち前記バイパス油路が分岐している箇所よりも油圧ポンプ側の箇所に設けられかつ前記蓄圧器に向けて圧油を送給する場合に開弁される第一開閉弁と、前記バイパス油路のうち前記油量増幅部の吐出部と前記常用油路との間に設けられかつ前記常用油路に向けた圧油を流す場合に開弁する第二開閉弁とを含むことを特徴とする請求項4に記載の蓄圧器を備えた油圧制御装置。 The shut-off mechanism is opened when pressure oil is provided to a location closer to the hydraulic pump than a location where the bypass oil passage branches out of the high-pressure side oil passage and pressure oil is fed toward the pressure accumulator. A first on-off valve that is provided between the discharge part of the oil amount amplifying part and the normal oil path in the bypass oil path, and is opened when pressure oil is directed toward the normal oil path. The hydraulic control apparatus provided with the pressure accumulator according to claim 4, further comprising two on-off valves.
- 前記第一開閉弁は、開弁に要する開弁力を弾性力によって所定値に設定されるとともに前記アキュムレータに向けた圧油の圧力がその開弁力以上になることにより開弁されかつアキュムレータに向けた方向とは反対の方向への圧油の流れに対しては閉弁してその流れを阻止する逆止弁を含むことを特徴とする請求項5に記載の蓄圧器を備えた油圧制御装置。 The first on-off valve is opened when the valve opening force required for valve opening is set to a predetermined value by an elastic force and the pressure of the pressure oil directed toward the accumulator exceeds the valve opening force. The hydraulic control with a pressure accumulator according to claim 5, further comprising a check valve that closes and blocks the flow of pressure oil in a direction opposite to the directed direction. apparatus.
- 前記第二開閉弁は、前記常用油路に向けた圧油によって開弁する逆止弁を含むことを特徴とする請求項5または6に記載の蓄圧器を備えた油圧制御装置。 The hydraulic control device with a pressure accumulator according to claim 5 or 6, wherein the second on-off valve includes a check valve that is opened by pressure oil directed toward the regular oil passage.
- 前記油圧ポンプを駆動するエンジンと、
モータによって駆動されて圧油を吐出する電動油圧ポンプと
を更に備え、
前記圧油追加手段は、前記油圧ポンプから前記蓄圧器に油圧が供給されている際に前記電動油圧ポンプが吐出した圧油を前記油圧常用部に供給するように切り替わる切替バルブを含む
ことを特徴とする請求項1に記載の蓄圧器を備えた油圧制御装置。 An engine for driving the hydraulic pump;
An electric hydraulic pump driven by a motor and discharging pressure oil;
The pressure oil adding means includes a switching valve that switches to supply the hydraulic oil discharged from the electric hydraulic pump to the hydraulic pressure portion when hydraulic pressure is supplied from the hydraulic pump to the pressure accumulator. A hydraulic control device comprising the pressure accumulator according to claim 1. - 前記切替バルブは、前記油圧ポンプが吐出した油圧が前記蓄圧器側に供給する圧力に調圧されていることにより前記電動油圧ポンプを前記油圧常用部に連通させ、前記油圧ポンプが吐出した油圧が前記蓄圧器側に供給する圧力より低い圧力に調圧されていることにより前記電動油圧ポンプを前記蓄圧器側に連通させるように切り替わるバルブを含むことを特徴とする請求項8に記載の蓄圧器を備えた油圧制御装置。 The switching valve causes the hydraulic pressure discharged from the hydraulic pump to communicate with the hydraulic service portion by adjusting the hydraulic pressure discharged from the hydraulic pump to a pressure supplied to the pressure accumulator side. 9. The pressure accumulator according to claim 8, further comprising a valve that is switched so as to communicate the electric hydraulic pump to the pressure accumulator side by being regulated to a pressure lower than a pressure supplied to the pressure accumulator side. Hydraulic control device with
- 前記油圧ポンプが吐出した圧油を前記蓄圧器側に供給する際に前記油圧ポンプから前記油圧常用部に供給される圧油の不足量を算出する不足量算出手段と、
この不足量算出手段で算出された前記圧油の不足量に基づいて前記電動油圧ポンプを制御する電動油圧ポンプ制御手段と
を備えていることを特徴とする請求項8または9に記載の蓄圧器を備えた油圧制御装置。 A shortage amount calculating means for calculating a shortage amount of pressure oil supplied from the hydraulic pump to the hydraulic regular portion when supplying the pressure oil discharged from the hydraulic pump to the accumulator side;
The pressure accumulator according to claim 8 or 9, further comprising: an electric hydraulic pump control unit that controls the electric hydraulic pump based on the shortage amount of the pressure oil calculated by the shortage amount calculating unit. Hydraulic control device with - 前記電動油圧ポンプは、回転数に応じて圧油を吐出するオイルポンプを含み、
前記電動油圧ポンプ制御手段は、前記不足量算出手段で算出された前記圧油の不足量を吐出するように前記電動油圧ポンプもしくは前記モータの回転数を制御する手段を含む
ことを特徴とする請求項10に記載の蓄圧器を備えた油圧制御装置。 The electric hydraulic pump includes an oil pump that discharges pressure oil according to the number of rotations,
The electric hydraulic pump control means includes means for controlling the rotational speed of the electric hydraulic pump or the motor so as to discharge the shortage of the pressure oil calculated by the shortage calculation means. Item 11. A hydraulic control device comprising the pressure accumulator according to Item 10. - 油圧によって係合および解放させられるロックアップクラッチを有する流体継手と、
そのロックアップクラッチを制御する油圧を発生させるロックアップ制御バルブと
を更に備え、
前記圧油追加手段は、前記ロックアップクラッチに供給される圧油によって駆動されることにより前記油圧常用部に供給される油量を増大させる油量増幅部を備えていることを特徴とする請求項1に記載の蓄圧器を備えた油圧制御装置。 A fluid coupling having a lock-up clutch that is engaged and released by hydraulic pressure;
A lockup control valve for generating a hydraulic pressure for controlling the lockup clutch,
The pressure oil adding means includes an oil amount amplifying unit that increases the amount of oil supplied to the hydraulic regular portion by being driven by pressure oil supplied to the lockup clutch. A hydraulic control device comprising the pressure accumulator according to Item 1. - 前記油量増幅部は、前記ロックアップクラッチに油圧を供給する油路と前記油圧常用部に圧油を供給する油路との間に配置され、前記ロックアップクラッチに向けて供給された圧油の一部を噴射させることに伴って生じる負圧でオイルを貯留部から汲み上げるジェットポンプを含むことを特徴とする請求項12に記載の蓄圧器を備えた油圧制御装置。 The oil amount amplifying unit is disposed between an oil passage that supplies hydraulic pressure to the lockup clutch and an oil passage that supplies pressure oil to the hydraulic regular portion, and is supplied to the lockup clutch 13. The hydraulic control device with a pressure accumulator according to claim 12, further comprising a jet pump that pumps oil from the storage portion with a negative pressure generated by injecting a part of the pressure.
- 前記ジェットポンプの流入口側に設けられ、前記蓄圧器側に供給する油圧が高い場合に開かれる前記ジェットポンプに対する圧油の供給を許容し、かつ前記蓄圧器側に供給する油圧が低い場合に閉じられて前記ジェットポンプに対する圧油の供給を遮断する切替バルブを更に備えていることを特徴とする請求項13に記載の蓄圧器を備えた油圧制御装置。 When the hydraulic pressure supplied to the pressure accumulator side is low and is allowed to be supplied to the jet pump that is provided on the inlet side of the jet pump and is opened when the hydraulic pressure supplied to the pressure accumulator side is high 14. The hydraulic control apparatus with a pressure accumulator according to claim 13, further comprising a switching valve that is closed to shut off supply of pressure oil to the jet pump.
- 前記油圧ポンプで発生した油圧を調圧する調圧バルブを更に備え、
その調圧バルブにおける調圧に伴って生じたドレイン油圧が前記油圧常用部に供給され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14のいずれかに記載の蓄圧器を備えた油圧制御装置。 A pressure regulating valve for regulating the hydraulic pressure generated by the hydraulic pump;
The pressure accumulator according to any one of claims 1 to 14, wherein a drain hydraulic pressure generated by pressure regulation in the pressure regulating valve is supplied to the hydraulic pressure regular part. Hydraulic control device. - 前記油圧常用部は、潤滑箇所とオイルによって冷却を行う冷却箇所との少なくともいずれか一方を含むことを特徴とする請求項1ないし15のいずれかに記載の蓄圧器を備えた油圧制御装置。 The hydraulic control apparatus with a pressure accumulator according to any one of claims 1 to 15, wherein the hydraulic regular part includes at least one of a lubrication point and a cooling point that is cooled by oil.
- 前記油圧ポンプで発生した油圧を調圧し、かつ調圧レベルに応じて信号圧を出力する調圧バルブを更に備え、
その調圧バルブにおける調圧に伴って生じたドレイン油圧が前記油圧常用部に供給されるように構成され、
前記切替バルブは、前記信号圧によって切り替え動作するバルブを含む
ことを特徴とする請求項7ないし11、14のいずれかに記載の蓄圧器を備えた油圧制御装置。 A pressure regulating valve that regulates the hydraulic pressure generated by the hydraulic pump and outputs a signal pressure according to the pressure regulating level;
The drain hydraulic pressure generated along with the pressure regulation in the pressure regulating valve is configured to be supplied to the hydraulic pressure regular part,
15. The hydraulic control apparatus with a pressure accumulator according to claim 7, wherein the switching valve includes a valve that is switched by the signal pressure.
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Also Published As
Publication number | Publication date |
---|---|
DE112011103673T5 (en) | 2013-09-26 |
US20130330216A1 (en) | 2013-12-12 |
DE112011103673T8 (en) | 2013-12-12 |
JPWO2012060117A1 (en) | 2014-05-12 |
CN103189672A (en) | 2013-07-03 |
JP5440714B2 (en) | 2014-03-12 |
CN103189672B (en) | 2015-07-29 |
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