JP3716757B2 - Oil pump control device and air mixing amount estimation device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an oil pump control device, and more particularly to an oil pump control device that can always supply an appropriate amount of hydraulic oil regardless of air mixing.
[0002]
[Prior art]
A belt-type continuously variable transmission that changes the gear ratio by changing the pulley groove width and the operating state of the clutch and brake are switched by a hydraulic actuator, while the belt is pinched by hydraulic pressure to transmit power. Various hydraulic power transmission devices are mounted on the vehicle, such as a hydraulic transmission in which a power transmission state such as a ratio (shift speed) and a forward / reverse movement is changed, and a hydraulic forward / reverse switching device. The vehicle power transmission device described in Japanese Patent Laid-Open No. 10-89445 is an example, and a predetermined amount of power is transmitted by an oil pump in order to change a power transmission state such as a gear ratio or to lubricate a rotating member such as a gear. Hydraulic oil is supplied.
[0003]
[Problems to be solved by the invention]
By the way, it is inevitable that air will be mixed into such hydraulic oil by agitation during lubrication. However, since such air mixing has not been considered in the past, the volume of the air is substantially reduced. There is a possibility that the supply amount of the hydraulic oil is insufficient, the lubrication performance is deteriorated, or the speed change speed is lowered without obtaining a desired hydraulic pressure. In addition, it is conceivable to increase the supply amount by a certain amount so that such a shortage of hydraulic oil does not occur. However, since the air mixing amount changes depending on conditions, more hydraulic oil than necessary is supplied in some cases. , Energy loss such as fuel consumption occurs due to excessive output of the oil pump.
[0004]
The present invention has been made against the background of the above circumstances, and the object of the present invention is to always supply an appropriate amount of hydraulic oil regardless of air mixing, while avoiding shortage of hydraulic oil. It is to reduce the energy loss due to the excessive output of the pump.
[0005]
[Means for Solving the Problems]
  In order to achieve this object, the first invention provides a power transmission device.Is used to lubricate the rotating member constituting the engine, and pumps up the hydraulic oil that is agitated as the rotating member rotates, to the hydraulic control system of the power transmission deviceIn the control device of the oil pump to be supplied,In consideration of the rotational speed of the rotating member and the operating oil temperature, the amount of air mixed in the hydraulic oil is obtained, and the required amount of oil is supplied regardless of the mixed air.The discharge amount of the oil pump is controlled.
  The “discharge amount” is a pressure-feeding flow rate of the hydraulic oil per unit time and includes air mixed in the hydraulic oil.
[0007]
  First2Invention is the firstMysteriousIn the oil pump control device, (a) required oil amount calculation means for obtaining the required oil amount of the hydraulic oil according to the operating state of the power transmission device; and (b)Rotational speed and hydraulic oil temperature of the rotating memberAnd (c) a discharge amount calculating means for determining a discharge amount of the oil pump based on the necessary oil amount and the air mixture amount. .
[0008]
  First3The invention is the first inventionOr the second inventionIn the oil pump control apparatus, the oil pump is rotationally driven by a dedicated electric motor.
[0010]
【The invention's effect】
  In such an oil pump control device, it is involved in air contamination of hydraulic oil.Determine the amount of air contamination taking into account the rotational speed and hydraulic oil temperature of the rotating member, and supply the required amount of oil regardless of the air contamination.Because the oil pump discharge rate is controlled, an appropriate amount of hydraulic oil is always supplied regardless of air contamination.To hydraulic control systemThus, energy loss due to excessive output of the oil pump can be reduced while avoiding shortage of hydraulic oil due to air mixing.
[0011]
  IeThe hydraulic oil is used to lubricate the rotating member constituting the power transmission device, and is stirred as the rotating member rotates.When,Air is mixed during the stirring, and the amount of mixing increases as the rotational speed of the rotating member increases.For,By controlling the discharge amount of the oil pump in consideration of the rotation speed of the rotating member, an appropriate amount of hydraulic oil is always supplied according to the air mixing amount.Become.
  In addition, when a defoaming agent is used in the hydraulic oil, the air mixing amount varies depending on the temperature characteristics of the defoaming agent. Generally, when the hydraulic oil temperature rises, the defoaming performance decreases and the air mixing amount decreases. Therefore, by controlling the discharge amount of the oil pump in consideration of the hydraulic oil temperature, an appropriate amount of hydraulic oil is always supplied regardless of an increase in the amount of air mixed with the temperature rise.
[0012]
  First2The invention relates to the case where the required oil amount is calculated according to the operating state of the power transmission device by the required oil amount calculating means and is involved in the air mixing by the air mixing amount calculating means.Rotating member rotation speed and hydraulic oil temperatureThe amount of air mixed is calculated based on the above, and the discharge amount of the oil pump is calculated from the required amount of oil and the amount of air mixed by the discharge amount calculating means. The required amount of hydraulic oil is supplied, and energy loss due to excessive output of the oil pump can be satisfactorily reduced while avoiding shortage of hydraulic oil due to air mixing.
[0013]
  First3In the invention, since the oil pump is rotationally driven by a dedicated electric motor, the discharge amount can be appropriately controlled with high accuracy in consideration of the air mixing amount without affecting other driving forces such as the vehicle driving force.
[0015]
DETAILED DESCRIPTION OF THE INVENTION
In the present invention, the operating state of the clutch and the brake is switched by a belt type continuously variable transmission that changes the gear ratio by changing the groove width of the pulley, and the hydraulic actuator while clamping the belt with hydraulic pressure. This makes it possible for vehicles such as hydraulic transmissions that change power transmission conditions such as gear ratios (shift speeds) and forward / reverse travel, hydraulic forward / reverse switching devices, and differential devices that distribute power to left and right drive wheels. It is suitably applied to an oil pump control device that supplies hydraulic oil to the power transmission device of each part, changes the power transmission state and lubricates each part, but supplies hydraulic oil to a power transmission device other than for vehicles. Various aspects can be adopted such as being applicable to the case where hydraulic oil is supplied to the power transmission device only for lubrication.
[0016]
  As the oil pump, a rotary pump such as a gear pump or a vane pump is preferably used, but various pumps such as a direct-acting pump can be employed. As a drive source for driving the oil pump,3Although it is desirable to employ a dedicated electric motor as in the invention, other driving sources such as an internal combustion engine capable of controlling the driving force can also be used. Moreover, what served also as drive sources other than an oil pump, such as a drive source for vehicle travel, may be used.
[0018]
  First2The air mixing amount estimation means of the invention is, for example, a physical quantity involved in air mixing.(Including the rotational speed of the rotating member and hydraulic oil temperature, the same applies hereinafter)It is configured to calculate the air mixing amount according to the actual physical quantity value based on the correlation (arithmetic expression, map, etc.) obtained by experiment in advance using as a parameter, or the theoretically derived arithmetic expression. . The relationship between the physical quantity and the air mixing amount is, for example, that the relationship between the discharge amount of the oil pump and the hydraulic pressure varies depending on the air mixing amount, so by obtaining the relationship between the discharge amount and the hydraulic pressure while changing the value of the physical quantity, The amount of air mixing can be estimated, and for example, a discharge amount that can generate a predetermined reference hydraulic pressure may be obtained.
[0019]
  Here, if the oil pressure itself is detected and the oil pump discharge amount is controlled, the influence of the air mixing amount can be reduced, but the oil pressure sensor is expensive and the detection accuracy decreases with time. Because2As in the invention, it is common to control the discharge amount by obtaining the required oil amount. Since the actual supply amount of hydraulic oil changes due to air mixing, the discharge amount is controlled in consideration of the air mixing amount. It is necessary to do. An air mixing rate can also be used as the air mixing amount.
[0020]
  First2In the present invention, the air mixing amount is obtained by the air mixing amount estimating means, and the discharge amount is calculated based on the air mixing amount and the required oil amount by the discharge amount calculating means, but according to the physical quantity involved in the air mixing amount. It is also possible to employ correction means for directly calculating the discharge amount reflecting the air mixing amount by correcting the necessary oil amount. Since the correction amount by the correction unit substantially corresponds to the air mixing amount, it is assumed that the correction unit in this case has both functions of the air mixing amount estimation unit and the discharge amount calculation unit. CanThis is an embodiment of the second invention.
[0021]
  The second2In the invention, the required oil amount is obtained according to the operating state of the power transmission device,FirstIn carrying out the invention, it may be a case where a certain required oil amount is determined in advance, such as a case where the required oil amount hardly changes regardless of the operating state. That is, according to the first aspect of the present invention, for example, the air mixing amount is obtained based on the physical amount involved in the air mixing of the hydraulic oil, and the discharge amount of the oil pump is controlled so that a predetermined required oil amount is supplied regardless of the air mixing. Configured to do.
[0022]
【Example】
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a schematic configuration diagram for explaining a hybrid drive control device 10 to which the present invention is applied. FIG. 2 is a skeleton diagram of a power transmission mechanism such as a transmission 12. The hybrid drive control device 10 It comprises an engine 14 that generates power by combustion, a motor generator 16 that is used as an electric motor and a generator, and a double pinion type planetary gear unit 18, and is placed horizontally in an FF (front engine / front drive) vehicle or the like. Used on board. The engine 14 is connected to the sun gear 18s of the planetary gear unit 18, the motor generator 16 is connected to the carrier 18c, and the ring gear 18r is connected to the case 20 via the first brake B1. The carrier 18c is connected to the input shaft 22 of the transmission 12 via the first clutch C1, and the ring gear 18r is connected to the input shaft 22 via the second clutch C2. The engine 14 is an internal combustion engine, and the planetary gear unit 18 is a gear differential that functions as a composite distribution mechanism.
[0023]
The clutches C1 and C2 and the first brake B1 are wet multi-plate hydraulic friction engagement devices that are frictionally engaged by a hydraulic actuator, and are frictionally engaged by hydraulic oil supplied from the hydraulic control circuit 24. It is like that. FIG. 3 is a diagram showing a main part of the hydraulic control circuit 24. The original pressure PC generated by the electric hydraulic pressure generator 26 including the electric pump is transferred to the shift lever 30 (see FIG. 1) via the manual valve 28. Is supplied to each of the clutches C1, C2 and the brake B1 according to the shift position. The shift lever 30 is a shift operation member that is operated by the driver. In this embodiment, the shift lever 30 is selected and operated in five shift positions of “B”, “D”, “N”, “R”, and “P”. The manual valve 28 is connected to the shift lever 30 via a cable, a link, or the like, and can be mechanically switched in accordance with the operation of the shift lever 30.
[0024]
The “B” position is a shift position in which a relatively large power source brake is generated due to a downshift of the transmission 12 during forward travel, and the “D” position is a shift position for forward travel. In these shift positions, The original pressure PC is supplied from the output port 28a to the clutches C1 and C2. The original pressure PC is supplied to the first clutch C <b> 1 via the shuttle valve 31. The “N” position is a shift position that cuts off power transmission from the power source, the “R” position is a shift position that travels backward, and the “P” position cuts off power transmission from the power source and is not shown in the drawing. The shift positions mechanically prevent the drive wheels from rotating, and at these shift positions, the original pressure PC is supplied from the output port 28b to the first brake B1. The original pressure PC output from the output port 28b is also input to the return port 28c. In the “R” position, the original pressure PC is supplied from the return port 28c to the first clutch C1 via the output port 28d. It has come to be.
[0025]
The clutches C1, C2 and the brake B1 are provided with control valves 32, 34, 36, respectively, and their hydraulic pressure P_C1, P_C2, P_B1Is to be controlled. Hydraulic pressure P of clutch C1_C1Is regulated by an ON-OFF valve 38, and the clutch C2 and the brake B1 are regulated by a linear solenoid valve 40.
[0026]
Then, according to the operating states of the clutches C1, C2 and the brake B1, the travel modes shown in FIG. 4 are established. That is, in the “B” position or the “D” position, any one of “ETC mode”, “direct connection mode”, and “motor traveling mode (forward)” is established, and in the “ETC mode”, the second clutch C2 is engaged. In a state where the first clutch C1 and the first brake B1 are disengaged and in other words, the sun gear 18s, the carrier 18c, and the ring gear 18r are relatively rotatable, the engine 14 and the motor generator 16 are operated together to operate the sun gear 18s. Torque is applied to the carrier 18c, and the ring gear 18r is rotated to move the vehicle forward. In the “direct connection mode”, the engine 14 is operated to drive the vehicle forward while the clutches C1 and C2 are engaged and the first brake B1 is released. In the “direct connection mode”, the motor generator 16 is subjected to power running control according to the storage amount (remaining capacity) SOC of the battery 42 (see FIG. 1), and the engine torque is reduced correspondingly, or the motor generator 16 is controlled to generate power. At the same time, by increasing the engine torque by that amount, the charged amount SOC is maintained within an appropriate range with excellent charge / discharge efficiency, for example. In the “motor running mode (forward)”, the motor generator 16 is operated to drive the vehicle forward while the first clutch C1 is engaged and the second clutch C2 and the first brake B1 are released. In the “motor running mode (forward)”, the motor generator 16 is regeneratively controlled when the accelerator is OFF, etc., so that the battery 42 can be charged by generating kinetic energy of the vehicle and a braking force can be applied to the vehicle. .
[0027]
In the “N” position or the “P” position, either “neutral” or “charging / Eng start mode” is established, and in “neutral”, all of the clutches C1, C2 and the first brake B1 are released. In the “charging / engage start mode”, the clutches C1 and C2 are disengaged and the first brake B1 is engaged, and the motor generator 16 is rotated in the reverse direction to start the engine 14, or the engine 14 passes through the planetary gear unit 18. Then, the motor generator 16 is driven to rotate and the power generation is controlled, thereby generating electric energy and charging the battery 42.
[0028]
In the “R” position, “motor travel mode (reverse)” or “friction travel mode” is established, and in “motor travel mode (reverse)”, the first clutch C1 is engaged and the second clutch C2 and the second clutch With the one brake B1 released, the motor generator 16 is rotationally driven in the reverse direction to reversely rotate the carrier 18c and further the input shaft 22, thereby causing the vehicle to travel backward. The “friction running mode” is executed when an assist request is issued during reverse running in the “motor running mode (reverse)”. The engine 14 is started to rotate the sun gear 18s in the forward direction, In a state where the ring gear 18r is rotated in the forward direction along with the rotation of the sun gear 18s, the first brake B1 is slip-engaged to limit the rotation of the ring gear 18r, thereby rotating the carrier 18c in the reverse direction. Assists reverse travel by applying force.
[0029]
The transmission 12 is a belt-type continuously variable transmission (CVT). Power is transmitted from the output shaft 44 to the ring gear 50 of the differential device 48 via the counter gear 46, and the differential device 48 transmits left and right drive wheels ( In this embodiment, power is distributed to the front wheels 52. The transmission 12 includes a pair of variable pulleys 12a and 12b, and a gear ratio γ (= input shaft rotational speed Nin) is obtained by changing the V groove width by the hydraulic cylinder of the primary side (input side) variable pulley 12a. / Output shaft rotational speed Nout) is continuously changed, and the belt clamping pressure (tension) is adjusted by the hydraulic cylinder of the variable pulley 12b on the secondary side (output side). The hydraulic control circuit 24 includes a circuit for controlling the speed ratio γ and belt tension of the transmission 12, and hydraulic oil is supplied from a common electric hydraulic pressure generator 26. The hydraulic oil of the hydraulic control circuit 24 is also accumulated in an oil pan 96 (see FIG. 5) to lubricate the planetary gear unit 18 and the differential unit 48, and a part is supplied to the motor generator 16 to be cooled. It has become.
[0030]
The hybrid drive control device 10 of this embodiment is controlled by the HVECU 60 shown in FIG. The HVECU 60 includes a CPU, a RAM, a ROM, and the like, and performs signal processing in accordance with a program stored in advance in the ROM while using a temporary storage function of the RAM, whereby an electronic throttle ECU 62, an engine ECU 64, an M / GECU 66, The T / MECU 68, the ON / OFF valve 38 of the hydraulic control circuit 24, the linear solenoid valve 40, the starter 70 of the engine 14 and the like are controlled. The electronic throttle ECU 62 controls the opening and closing of the electronic throttle valve 72 of the engine 14, the engine ECU 64 controls the engine output by the fuel injection amount of the engine 14, the variable valve timing mechanism, the ignition timing, etc. The M / GECU 66 is an inverter. A power running torque, a regenerative braking torque, and the like of the motor generator 16 are controlled via 74, and a T / MECU 68 controls a speed ratio γ of the transmission 12, a belt tension, and the like. The starter 70 is a motor generator that functions as an electric motor and a generator, and is connected to the crankshaft of the engine 14 via a power transmission device such as a belt or a chain.
[0031]
The HVECU 60 is supplied with a signal indicating the operation amount θac of the accelerator pedal 78 as an accelerator operation member from the accelerator operation amount sensor 76 and a signal indicating the shift position of the shift lever 30 from the shift position sensor 80. . In addition, the engine rotation speed sensor 82, the motor rotation speed sensor 84, the input shaft rotation speed sensor 86, the output shaft rotation speed sensor 88, the CVT oil temperature sensor 90, and the cooling water temperature sensor 91 are respectively connected to the engine rotation speed (rotation speed) Ne Motor rotation speed (number of rotations) Nm, input shaft rotation speed (rotation speed of the input shaft 22) Nin, output shaft rotation speed (rotation speed of the output shaft 44) Nout, hydraulic oil temperature TH of the hydraulic control circuit 24_CVT, Cooling water temperature TH of engine 14_WAre respectively provided. The CVT oil temperature sensor 90 corresponds to hydraulic oil temperature detecting means, and the output shaft rotational speed Nout corresponds to the vehicle speed V. In addition, various signals representing the operation state such as the storage amount SOC of the battery 42 are supplied. The storage amount SOC may be simply a battery voltage, or may be obtained by sequentially integrating the charge / discharge amount. The accelerator operation amount θac corresponds to the driver's requested output amount.
[0032]
FIG. 5 is a block diagram illustrating a schematic configuration of the hydraulic control circuit 24. The transaxle 92 includes the transmission 12, the planetary gear unit 18, the differential unit 48, and the like, and a hydraulic control system 94 therein. Are hydraulic cylinders for shifting the transmission 12 and for clamping the belt, hydraulic actuators such as the first brake B1 and clutches C1 and C2 of the planetary gear unit 18, the ON-OFF valve 38, the linear solenoid valve 40, and the like. An electromagnetic switching valve, a hydraulic control valve, or the like that is electrically controlled by the HVECU 60. The hydraulic oil in the oil pan 96 is pumped up by the oil pump 100 and supplied to the hydraulic control system 94 to operate the hydraulic actuator, while the surplus is used for lubrication of each part in the transaxle 92. , Part of the oil is circulated to the oil cooler 114 and the hydraulic oil temperature TH_CVTIs adjusted. The transaxle 92 corresponds to a vehicle power transmission device, and the planetary gear unit 18 and the transmission 12 in which power transmission is performed via hydraulic pressure correspond to a hydraulic power transmission device.
[0033]
The oil pump 100 is a rotary pump such as a gear pump, and is rotated by a dedicated electric motor 98. The oil pressure generator 26 includes the oil pump 100 and the electric motor 98. Has been. The electric motor 98 is controlled by the HVECU 60, and the motor rotational speed N is determined from the rotational speed sensor 102 such as a resolver and the ammeter 104._PM, Drive current I corresponding to motor torque_PMAre respectively supplied to the HVECU 60. Motor rotation speed N_PMCorresponds to the pump rotation speed, that is, the discharge amount of the oil pump 100, and the drive current I corresponding to the motor torque._PMCorresponds to the driving force of the oil pump 100 and the generated hydraulic pressure. The hydraulic control circuit 24 corresponds to a hydraulic circuit, and includes a HVECU 60, an electric motor 98, and an oil pump 100 to constitute a hydraulic control device.
[0034]
FIG. 6 shows a line oil pressure P that is the basis of the original pressure PC in the oil pressure control circuit 24._LThe hydraulic oil sucked up by the oil pump 100 through the strainer 106 is a predetermined line oil pressure P by a primary regulator valve 108 that functions as a pressure control valve._LPressure is adjusted. The primary regulator valve 108 has a signal pressure P of the linear solenoid valve 110 duty-controlled by the HVECU 60._SLSIs supplied, and its signal pressure P_SLSDepending on the line oil pressure P_LIs controlled, and excess hydraulic oil is drained to the oil passage 112. Line hydraulic pressure P_LIs used as a basis for the original pressure PC, and is also used for the shift control of the transmission 12 and the belt clamping pressure. P_L ^*The pressure is adjusted to be The hydraulic oil in the oil passage 112 is supplied to the lubricating parts of each part of the hydraulic control circuit 24, and a part of the hydraulic oil is supplied to the oil cooler 114 to be cooled. The pressure is adjusted to a predetermined hydraulic pressure by a pressure regulating valve 116 so as to be supplied to the oil cooler 114.
[0035]
FIG. 7 is a flowchart for explaining the operation of the oil pump 100, which functions as an oil pump control device, and is repeatedly executed at a predetermined cycle time by signal processing of the HVECU 60. In step S1, the required oil flow rate Q is calculated according to the operating state of the transaxle 92. The required oil flow rate Q is basically obtained by adding the leakage amount of the hydraulic control circuit 24, the cooler circulation flow rate, and the lubrication flow rate, and at the time of shifting of the transmission 12, switching of the traveling mode of FIG. When hydraulic fluid is used, the amount of increase is corrected. The amount of leakage increases as the hydraulic fluid viscosity is low and increases as the hydraulic pressure increases._CVTDrive current I corresponding to pressure and hydraulic pressure_PMIs obtained from a predetermined map, arithmetic expression, or the like. The lubrication flow rate and the cooler circulation flow rate are the input shaft rotational speed N_inAnd output shaft speed N_out, Hydraulic oil temperature TH_CVTThe throttle valve opening corresponding to the engine output is obtained as a parameter. The required oil flow rate Q corresponds to the required oil amount, and the portion of the series of signal processing performed by the HVECU 60 that executes step S1 functions as the required oil amount calculating means.
[0036]
  In step S2, the input shaft rotational speed Nin, the output shaft rotational speed Nout, and the hydraulic oil temperature TH_CVTAnd the drive current I corresponding to the hydraulic pressure_PMBased on a predetermined data map using as a parameter, the air mixing ratio R into the hydraulic fluid from those actual values_AIs calculated. In the present embodiment, the planetary gear unit 18 and the differential unit 48 are immersed and lubricated in the hydraulic oil in the oil pan 96, so that they are agitated and scraped up with their rotation. The air mixing rate R increases as the rotation speed increases._ATherefore, the input shaft rotational speed Nin and the output shaft rotational speed Nout corresponding to these rotational speeds are the air mixing rate R._AAffects. In addition, an antifoaming agent is used to suppress the generation of bubbles, but the antifoaming agent has a hydraulic oil temperature TH._CVTThe higher the value, the lower the performance and the air mixing rate R_AThe oil temperature TH_CVTDepending on the air mixing rate R_AChanges. The planetary gear unit 18 and the differential unit 48 are rotating members that are lubricated by hydraulic oil, and the portion of the series of signal processing performed by the HVECU 60 that executes step S2 is an air mixing amount estimation unit.SteppedAnd functioning. Air mixing rate R_ACorresponds to the air mixing amount.
[0037]
Input shaft rotational speed Nin, output shaft rotational speed Nout, hydraulic oil temperature TH_CVT, And drive current I_PMIs a physical quantity related to the air mixing amount, and the air mixing rate R based on these physical quantities_AA data map for obtaining is obtained in advance by experiments. That is, the pump rotational speed N of the oil pump 100_PThe relationship between the discharge amount and the generated hydraulic pressure is the air mixing rate R_AThe pump rotation speed N that generates a predetermined reference hydraulic pressure while changing the value of each physical quantity_P, The pump rotation speed N_PIs the air mixing rate R_AThe air mixing rate R using these physical quantities as parameters_AA data map can be created.
[0038]
In step S3, the required oil flow rate Q obtained in step S1 and the air mixing rate R obtained in step S2._ARequired oil pumping amount Q^*Is calculated. Specifically, the required oil pumping amount Q is added to the required oil flow rate Q by the air mixing amount.^*The required amount of oil pumped by the oil pump 100 is Q.^*As the hydraulic oil containing a predetermined amount of air is pumped up and discharged, the necessary oil flow rate Q is pumped as a substantial hydraulic oil amount excluding air. The amount of oil pumped up corresponds to the discharge amount, and the part that executes step S3 in the series of signal processing by the HVECU 60 functions as a discharge amount calculation means.
[0039]
In step S4, the hydraulic oil temperature TH_CVTDrive current I corresponding to pressure and hydraulic pressure_PM, Pump rotation speed, ie motor rotation speed N_PMThe pump volumetric efficiency η is obtained based on the above, and in step S5, the required oil pumping amount Q^*And required oil pumping volume Q based on pump volumetric efficiency η^*Target pump rotational speed N at which hydraulic oil is discharged at a discharge amount of_P ^*Is calculated. In the last step S6, the target pump rotational speed N_P ^*The target drive current I of the electric motor 98 is adjusted so that the oil pump 100 rotates._PM ^*Is calculated and output. That is, the actual motor rotation speed N_PMIs the target pump speed N_P ^*So that the rotational speed corresponding to the target drive current I_PM ^*And the target drive current I_PM ^*Thus, the electric motor 98 is operated.
[0040]
Thus, in this embodiment, the required oil flow rate Q is obtained according to the operating state of the transaxle 92 (S1), and the air mixing rate R is based on the physical quantity involved in air mixing._A(S2), required oil flow rate Q and air mixing rate R_ARequired oil pumping amount Q^*Is calculated (S3), and the required oil pumping amount Q^*Since the oil pump 100 is controlled so as to be discharged at the same time, the hydraulic oil at the required oil flow rate Q is always supplied regardless of air mixing, and the shortage of hydraulic oil due to air mixing is avoided. However, energy loss due to excessive output of the electric motor 98 is reduced, and fuel efficiency is improved.
[0041]
That is, the physical quantity involved in the air mixing of the hydraulic oil, specifically the input shaft rotational speed Nin, the output shaft rotational speed Nout, the hydraulic oil temperature TH_CVTAnd the drive current I corresponding to the hydraulic pressure_PM, As a parameter, the air mixing rate R from a predetermined data map_AThe air mixing rate R_AThe amount of oil pump 100 discharged, that is, the required oil pumping amount Q^*Therefore, an appropriate amount of hydraulic fluid is always supplied regardless of air contamination. Specifically, since hydraulic oil is used for lubrication of the planetary gear unit 18 and the differential unit 48, air is mixed by being agitated as they rotate, but this corresponds to their rotational speed. Since the discharge amount of the oil pump 100 is controlled in consideration of the input shaft rotation speed Nin and the output shaft rotation speed Nout, an appropriate amount of hydraulic oil is always supplied regardless of air mixing during stirring. Further, in the hydraulic oil of this example, the generation of bubbles is suppressed by the antifoaming agent, and the hydraulic oil temperature TH_CVTThe defoaming performance declines as the air quality increases, and the air mixing rate R_AThe hydraulic oil temperature TH_{CV T}Since the discharge amount of the oil pump 100 is controlled in consideration of the_ARegardless of the increase, the appropriate amount of hydraulic oil is always supplied.
[0042]
Also, input shaft rotational speed Nin, output shaft rotational speed Nout, hydraulic oil temperature TH_CVTAnd the drive current I corresponding to the hydraulic pressure_PMThe air mixing rate R from a predetermined data map based on_AThe air mixing rate R, which is difficult to measure, is calculated._ACan be obtained by a simple technique.
[0043]
In this embodiment, since the oil pump 100 is rotationally driven by the dedicated electric motor 98, the discharge amount can be set with high accuracy in consideration of the air mixing amount without affecting other driving force such as vehicle driving force. It can be controlled properly.
[0044]
As mentioned above, although the Example of this invention was described in detail based on drawing, this is an embodiment to the last, and this invention implements in the aspect which added various change and improvement based on the knowledge of those skilled in the art. Can do.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram illustrating a hybrid drive control device including an oil pump control device according to an embodiment of the present invention.
FIG. 2 is a skeleton diagram showing a power transmission system of the hybrid drive control device of FIG. 1;
FIG. 3 is a circuit diagram showing a part of the hydraulic control circuit of FIG. 1;
4 is a diagram for explaining the relationship between several travel modes established in the hybrid drive control device of FIG. 1 and the operating states of clutches and brakes.
FIG. 5 is a block diagram illustrating a schematic configuration of a hydraulic control circuit in FIG. 1;
6 is a circuit diagram specifically showing a hydraulic pressure generating portion of the hydraulic control circuit of FIG. 5. FIG.
7 is a flowchart for explaining the operation of an oil pump of the hydraulic control circuit of FIG. 5;
[Explanation of symbols]
  18: Planetary gear device (rotating member) 48: Differential device (rotating member) 60: HVECU 92: Transaxle (power transmission device) 98: Electric motor 100: Oil pump R_A: Air mixing rate (air mixing amount) Nin: Input shaft rotation speedEvery time    Nout: Output shaft rotation speedEvery time    TH_CVT: Hydraulic oil temperatureEvery time
Step S1: Required oil amount calculation means
Step S2: Air mixing amount estimation handSteps
Step S3: Discharge amount calculation means

Claims (3)

In a control apparatus for an oil pump that is used to lubricate a rotating member constituting a power transmission device, pumps up hydraulic oil that is agitated as the rotary member rotates and supplies the hydraulic oil to a hydraulic control system of the power transmission device. ,
Determining the amount of air contamination of the hydraulic oil in consideration of the rotational speed of the rotating member and the temperature of the hydraulic oil, and controlling the discharge amount of the oil pump so that the required amount of oil is supplied regardless of the air contamination. Oil pump control device. A required oil amount calculating means for determining a required oil amount of the hydraulic oil according to an operating state of the power transmission device;
An air mixing amount estimation means for obtaining an air mixing amount based on the rotational speed and hydraulic oil temperature of the rotating member;
The oil pump control device according to claim 1, further comprising: a discharge amount calculating unit that calculates a discharge amount of the oil pump based on the required oil amount and the air mixing amount. The oil pump is an oil pump control equipment according to claim 1 or 2, characterized in that rotationally driven by a dedicated electric motor.

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