JP2003097677A - Power transmission lubrication system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further reduce an energy loss of an oil pump by controlling a supply amount of lubricating oil to a minimum as required according to an operating state of a belt type continuously variable transmission. SOLUTION: The energy loss of the transmission efficiency η of the belt type continuously variable transmission is regarded as heat energy converted by heating caused by friction of a transmission belt or the like, and the supply amount QOIL of operating oil for lubricating a belt is controlled based on the transmission efficiency η which varies according to the operating state of the belt type continuously variable transmission. By this, lubrication of the belt can be always equally and properly controlled to a different heating amount according to the operating state, and the energy loss of the oil pump caused by excessive supply of the lubricating oil is reduced, as a result, the fuel consumption is improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubricating device for a power transmission mechanism, and more particularly to controlling the amount of lubricating oil supplied to a necessary minimum according to the operating state of the power transmission mechanism to reduce energy loss in an oil pump or the like. The present invention relates to a technique for reducing the above.

[0002]

2. Description of the Related Art A belt type continuously variable transmission in which a transmission belt is wound around a pair of variable pulleys whose groove width can be changed is used in an automatic transmission for vehicles. The continuously variable transmission is configured with, for example, a transmission belt due to the vibration of the belt, the shape change between the circular arc portion wound around the pulley and the straight portion located between the pulleys, and the winding and unwinding of the pulley. Generates heat due to frictional contact between many blocks, frictional contact between blocks and variable pulley, and mutual frictional contact between many layered thin metal plates that make up the hoop of a transmission belt. Inevitably, lubricating oil is sprinkled on transmission belts to prevent overheating. The device described in Japanese Patent Application Laid-Open No. 1-269761 is an example of such a device. By temporarily increasing the supply amount of lubricating oil when the input torque is rapidly increased, which is likely to generate heat due to belt slip, other types of oil can be used. Energy loss is reduced by lowering the pressure generated by the pump.

[0003]

By the way, in such a belt type continuously variable transmission, the transmission efficiency varies depending on the operating conditions such as the gear ratio, the input rotation speed, the input torque, and the belt clamping pressure. Although the calorific value changes depending on the difference, the conventional lubricating device does not consider the transmission efficiency at all, and therefore energy loss due to excessive supply of lubricating oil is still unavoidable, which is not always satisfactory.

The present invention has been made in view of the above circumstances. An object of the present invention is to control the supply amount of lubricating oil to a necessary minimum according to the operating state of a belt type continuously variable transmission. It is to further reduce the energy loss of the oil pump.

[0005]

In order to achieve the above object, the first aspect of the present invention provides a power transmission mechanism having a heat generating portion that generates heat in accordance with an operating state to supply lubricating oil by an oil pump to prevent overheating. A lubrication device for preventing a lubricating oil supply amount control means for controlling a supply amount of the lubricating oil in consideration of a transmission efficiency that changes according to an operating state of the power transmission mechanism.

A second aspect of the present invention is the lubricating device for a power transmission mechanism according to the first aspect, wherein the lubricating oil supply amount control means is
(a) Transmission efficiency calculation means for obtaining transmission efficiency according to the operating state of the power transmission mechanism, and (b) Heat generation amount calculation means for calculating heat generation amount based on the transmission efficiency obtained by the transmission efficiency calculation means. And (c) the calorific value obtained by the calorific value calculation means, the temperature difference between the preset target temperature and the actual oil temperature of the lubricating oil used for lubrication, and the specific heat of the lubricating oil. And a discharge amount control means for controlling the discharge amount of the oil pump according to the supply amount calculated by the supply amount calculation means. And are included.

A third aspect of the present invention is the lubricating device for a power transmission mechanism according to the first or second aspect, wherein the power transmission mechanism is
It is a belt type continuously variable transmission in which a transmission belt is wound around a pair of variable pulleys whose groove width can be changed.

According to a fourth aspect of the present invention, in the lubricating device for a power transmission mechanism according to the third aspect of the present invention, the lubricating oil supply amount control means includes a gear ratio of the belt type continuously variable transmission and an input rotation of the belt type continuously variable transmission. Speed, its input torque of belt type continuously variable transmission,
And the transmission efficiency is obtained based on at least one of the belt clamping pressures of the belt type continuously variable transmission.

A fifth invention is characterized in that, in the lubricating device for a power transmission mechanism according to any one of the first to fourth inventions, the oil pump is rotationally driven by a dedicated electric motor.

[0010]

That is, since the transmission efficiency of the power transmission mechanism reflects the energy loss due to heat generation, the supply amount of the lubricating oil is controlled in consideration of the transmission efficiency which changes according to the operating state of the power transmission mechanism. As a result, it becomes possible to appropriately control the amount of lubricating oil supplied with respect to the amount of heat generation that differs depending on the operating state, and it is possible to reduce energy loss in the oil pump due to excessive supply of lubricating oil.

According to the second aspect of the invention, the transmission efficiency calculating means calculates the transmission efficiency according to the operating state of the power transmission mechanism, and the heat generation amount calculating means calculates the heat generation amount based on the transmission efficiency. The supply amount of the lubricating oil is calculated by the supply amount calculation means based on the temperature difference between the predetermined set temperature and the actual oil temperature of the lubricating oil used for lubrication, and the specific heat of the lubricating oil. The discharge amount of the oil pump is controlled according to the amount. Therefore, regardless of the transmission efficiency that changes sequentially according to the operating state of the power transmission mechanism, and also the amount of heat generation, the supply amount of lubricating oil and the discharge amount of the oil pump so that the temperature of the power transmission mechanism reaches the set target temperature. Is controlled, overheating of the power transmission mechanism is prevented, and the supply amount of lubricating oil is controlled to a necessary minimum, thereby reducing energy loss of the oil pump.

A third aspect of the present invention relates to a belt type continuously variable transmission in which a transmission belt is wound around a pair of variable pulleys whose groove width can be changed, and heat is generated by frictional contact between the transmission belt and the variable pulley. In addition, the amount of heat generated varies depending on the gear ratio, the input rotation speed, the input torque, or the belt clamping pressure, and the transmission efficiency changes depending on the amount of heat generated.
Therefore, as in the fourth aspect of the invention, the transmission efficiency can be obtained with high accuracy using the gear ratio, the input rotation speed, the input torque, or the belt clamping pressure as parameters, and the heat generation amount can be determined based on the transmission efficiency. It is possible to control the supply amount of the corresponding lubricating oil with high accuracy.

In the fifth aspect of the invention, since the oil pump is rotationally driven by the dedicated electric motor, the electric motor is driven according to the required supply amount of the lubricating oil without affecting other driving force such as vehicle driving force. By controlling the current,
Energy loss due to excessive supply of lubricating oil can be reduced.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION The present invention is preferably applied to a belt type continuously variable transmission for a vehicle, but generally in a power transmission mechanism other than the belt type continuously variable transmission, heat is generated due to frictional contact and the like. The present invention can be similarly applied because the transmission efficiency decreases depending on the amount of heat generation. For example, it can be applied to lubrication of a starting clutch and a lockup clutch of a torque converter, and transmission efficiency is required from input torque and clutch hydraulic pressure.

The lubricating oil supplied to the power transmission mechanism is sprayed from a nozzle or the like to a heat generating portion such as a power transmission belt, but even if it is allowed to flow through a cooling oil passage provided in the heat generating portion. good.

The transmission efficiency calculation means of the second aspect of the invention is configured to determine the transmission efficiency according to a predetermined data map or a calculation formula using the operating state such as the gear ratio as a parameter. The calorific value calculation means is configured to calculate the calorific value assuming that the energy loss amount of the transmission efficiency is consumed for the heat generation, for example, and is appropriately determined according to the heat generating mechanism of the power transmission mechanism. In addition to the temperature difference between the set target temperature and the oil temperature and the specific heat, the supply amount calculation means further considers the heat exchange efficiency that differs depending on the cooling mode by the lubricating oil, the outside air temperature related to heat dissipation, etc. It is also possible to obtain the supply amount with accuracy. In order to reliably prevent seizure due to overheating, it is desirable that the lubricating oil supply amount be set to be slightly larger in consideration of predetermined safety.

When the oil pump is used exclusively for lubrication of the power transmission mechanism, it is sufficient to control the discharge amount of the oil pump by the discharge amount control means, but the discharged lubricating oil is supplied to other than the power transmission mechanism. In this case, a flow rate adjusting means is provided for adjusting the flow rate of the lubricating oil supplied to the power transmission mechanism according to the supply amount obtained by the supply amount calculating means. The flow rate adjusting means may control the flow rate by increasing / decreasing the flow cross-sectional area of the lubricating oil, but the flow rate is controlled by controlling the hydraulic pressure of the flow rate adjusting part where the flow of the lubricating oil to the power transmission mechanism side is restricted by the orifice. It is also possible to employ various modes such as control of

It is desirable that the oil pump be rotationally driven by using a dedicated electric motor as in the fifth aspect of the invention, but if a variable displacement pump that can change the discharge amount independently of the rotation speed is used. Alternatively, for example, it may be rotationally driven by a driving force source for vehicle running such as an engine, and in that case, fuel consumption can be improved by controlling the output of the driving force source according to the discharge amount. .

According to the fourth aspect of the invention, the transmission efficiency is obtained based on at least one of the gear ratio, the input rotation speed, the input torque, and the belt clamping pressure of the belt type continuously variable transmission. It is desirable to obtain the transmission efficiency using all parameters.

[0020]

Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a schematic configuration diagram illustrating a hybrid drive control device 10 to which the present invention is applied, and FIG. 2 is a skeleton diagram including a belt-type continuously variable transmission 12. It comprises an engine 14 that generates power by combustion, a motor generator 16 used as an electric motor and a generator, and a double-pinion type planetary gear device 18, and is used by being horizontally installed in a vehicle. An engine 14 such as an internal combustion engine is connected to the sun gear 18s of the planetary gear device 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. Further, the carrier 18c is connected to the input shaft 22 of the belt type continuously variable transmission 12 via the first clutch C1, and the ring gear 18r is connected to the second gear.
The input shaft 22 is connected via the clutch C2. The engine 14 and the motor generator 16 are driving force sources for traveling the vehicle.

The clutches C1 and C2 and the first brake B1 are all wet type multi-plate hydraulic friction engagement devices that are frictionally engaged by a hydraulic actuator, and are frictionally engaged by operating oil supplied from the hydraulic control circuit 24. By being combined, each traveling mode shown in FIG. 3 is established according to the shift position of the shift lever 30.
The shift lever 30 is a shift operation member operated by a driver, and in the present embodiment, “B”, “D”, “N”,
There are five shift positions of "R" and "P" that can be selectively operated. The "B" and "D" positions are both forward shift positions, and the "B" position is a belt type stepless type. A relatively large driving force source brake is generated by a downshift of the transmission 12 or the like. The “N” position is a shift position that cuts off power transmission from the driving force source, the “R” position is a shift position that runs backward, and the “P” position cuts off power transmission from the driving power source and is not shown in the parking. This is a shift position in which the lock device mechanically blocks the rotation of the drive wheels.

At the "B" position or the "D" position, any one of the "ETC traveling mode", the "direct coupling traveling mode", and the "motor traveling mode (forward)" is established, and the "ETC traveling mode". Then, in the state where the second clutch C2 is engaged and the first clutch C1 and the first brake B1 are released, 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 Are actuated together to apply torque to the sun gear 18s and the carrier 18c to rotate the ring gear 18r to cause the vehicle to travel forward. In "Direct drive mode",
Engage the clutches C1 and C2 and connect the first brake B
With 1 open, the engine 14 is operated to drive the vehicle forward. Also, "motor drive mode (forward)"
Then, with the first clutch C1 engaged and the second clutch C2 and the first brake B1 released, the motor generator 16 is operated to cause the vehicle to travel forward. In the "motor running mode (forward)", the motor generator 16 is regeneratively controlled when the accelerator is off to generate the kinetic energy of the vehicle to charge the battery 42 (see FIG. 1) and to apply the braking force to the vehicle. Can be generated.

At the "N" position or the "P" position, either "neutral" or "charging / eng starting mode" is established, and at "neutral", all of the clutches C1 and C2 and the first brake B1 are opened. To do. In "Charge / Eng start mode", clutch C
1 and C2 are released, the first brake B1 is engaged, the motor generator 16 is rotated in the reverse direction, and the engine 1
4 is started, or the planetary gear unit 18 is driven by the engine 14.
The motor generator 16 is rotationally driven via the motor generator 16, and the motor generator 16 is regeneratively controlled to generate electric power to charge the battery 42.

At the "R" position, the "motor drive mode (reverse)" or the "friction drive mode" is established. In the "motor drive mode (reverse)", the first clutch C1 is engaged and the second clutch is engaged. With C2 and the first brake B1 released, the motor generator 16 is rotationally driven in the reverse direction to rotate the carrier 18c and further the input shaft 22 in the reverse direction, thereby causing the vehicle to travel backward. The "friction drive mode" is the first clutch C1.
And the second clutch C2 is disengaged and the engine 14 is operated to rotate the sun gear 18s in the positive direction, and the ring gear 18r is rotated in the positive direction as the sun gear 18s rotates. Then, the first brake B1 is slip-engaged to limit the rotation of the ring gear 18r, so that the carrier 18
Reverse rotation is applied to c to perform reverse traveling, and at the same time, the motor generator 16 may be rotationally driven in the reverse direction (power running control).

The belt type continuously variable transmission 12 is provided with a pair of variable pulleys 12a and 12b whose groove width can be changed and a transmission belt 32 wound around them, and the transmission belt 32 is shown in FIG. As shown, it is composed of a large number of blocks 34 and a pair of endless annular hoops 36. The block 34 is a thick plate-shaped metal member, and the hoops 36 are inserted into a pair of notches provided on both sides of the block 34 so that the blocks 34 contact each other in the plate thickness direction along the hoop 36. The two pulleys 12a and 12b are arranged in series in an annular shape, and both side surfaces are brought into frictional contact with the groove wall surfaces of the variable pulleys 12a and 12b and are rotated together, so that power is transmitted between the variable pulleys 12a and 12b. Hoop 3
6 is a stack of a plurality of endless annular metal thin plates 38 having a substantially uniform width dimension, for example, about 9 to 12 sheets. Then, by changing the V groove width by the hydraulic cylinder of the primary side (input side) variable pulley 12a, the engagement diameter of the transmission belt 32 with respect to both the variable pulleys 12a and 12b changes, and the gear ratio γ (= input rotation The speed Nin / output rotation 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 gear ratio γ and the belt tension of the belt type continuously variable transmission 12.

Power is transmitted from the output shaft 44 of the belt type continuously variable transmission 12 to the ring gear 50 of the differential gear 48 via the counter gear 46, and the left and right drive wheels (front wheels) 52 are transmitted by the differential gear 48. Power is distributed to.

Hybrid drive controller 10 of the present embodiment
The traveling mode is switched by the HVECU 60 shown in FIG. HVECU 60 is C
The electronic throttle ECU 62, the engine ECU 64, and the M / GECU 6 are equipped with a PU, a RAM, a ROM, etc., and execute signal processing according to a program stored in advance in the ROM while utilizing the temporary storage function of the RAM.
6, the T / MECU 68, the starter 70 of the engine 14, and the like are controlled. The electronic throttle ECU 62 is the engine 1
4 controls the opening and closing of the electronic throttle valve 72 of the engine 4, 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 controls the motor output via the inverter 74. The power running torque and the regenerative torque of the generator 16 are controlled, and the T / MECU 68 controls the gear ratio γ and the belt tension of the belt type continuously variable transmission 12.

The HVECU 60 is supplied with a signal from the accelerator operation amount sensor 76, which indicates the operation amount θac of the accelerator pedal 78 as an accelerator operation member.
A signal indicating the operation position (shift position) of the shift lever 30 is supplied from the shift position sensor 80. Further, the engine rotation speed sensor 82, the motor rotation speed sensor 84, the input rotation speed sensor 86, the output rotation speed sensor 88, the oil temperature sensor 90, the input torque sensor 92.
From the engine rotation speed (revolution speed) Ne, the motor rotation speed (revolution speed) Nm, and the input rotation speed (input shaft 22).
Rotation speed) Nin, output rotation speed (rotation speed of output shaft 44) Nout, oil temperature t _OIL of hydraulic oil (lubricant oil) in hydraulic control circuit 24, input torque (torque of input shaft 22) Tin Is supplied. These signals are supplied to the ECUs 62, 64, 66, 68 and the like as needed. The output rotation speed Nout corresponds to the vehicle speed V, and the accelerator operation amount θac represents the driver's output request amount. Instead of detecting the input torque Tin by the input torque sensor 92, the input torque Tin is calculated and obtained (estimated) from the torque of the engine 14 and the motor generator 16, the gear ratio ρ of the planetary gear device 18, and the like. Is also good.

For the shift control of the belt type continuously variable transmission 12 by the T / MECU 68, for example, as shown in FIG. 5, a map determined in advance using the accelerator operation amount θac and the vehicle speed V (corresponding to the output rotation speed Nout) as parameters. The target input rotation speed NINT is calculated from the actual input rotation speed N
This is performed by feedback-controlling the hydraulic pressure of the hydraulic cylinder of the primary side variable pulley 12a so that in matches the target input rotation speed NINT. In FIG. 5, γmax is the maximum gear ratio and γmin is the minimum gear ratio.

Control of the belt clamping pressure of the belt type continuously variable transmission 12, that is, the secondary side variable pulley 12
In order to prevent the transmission belt 32 from slipping, hydraulic control of the hydraulic cylinder b is required from a map predetermined with the accelerator operation amount θac and the gear ratio γ corresponding to the transmission torque as parameters, for example, as shown in FIG. The hydraulic pressure Pd is calculated, and the hydraulic pressure of the hydraulic cylinder of the secondary side variable pulley 12b is set to the required hydraulic pressure Pd by duty control of the linear solenoid valve or the like. Hydraulic pressure Pd
Belt clamping force, namely variable pulley 1
The frictional force between 2a, 12b and the transmission belt 32 is increased, belt slippage is prevented, and the transmission torque capacity is increased. The required oil pressure Pd can be obtained by using the input torque Tin instead of the accelerator operation amount θac.

On the other hand, FIG. 7 is a block diagram for explaining the schematic construction of the hydraulic control circuit 24. In FIG.
Reference numeral 02 denotes the belt type continuously variable transmission 12 and the planetary gear device 1.
8, a differential device 48, etc., and the hydraulic control system 104 therein includes the first brake B1 and the clutches C1, C.
2, hydraulic actuators such as the hydraulic cylinders of the belt type continuously variable transmission 12, and electromagnetic type switching valves and hydraulic control valves for switching the hydraulic circuits to establish the respective running modes. The hydraulic oil (also functioning as lubricating oil) in the oil pan 106 is the oil pump 10.
8 is pumped up and supplied to the hydraulic control system 104 to operate the hydraulic actuator and used for lubrication of each part in the transaxle 102.
The oil pump 108 is a rotary pump such as a gear pump, and is rotated and driven by a dedicated electric motor 110 supplied with electric power from the battery 42. The oil pump 108 and the electric motor 11
An electric oil pressure generating device including 0 is configured. The electric motor 110 is controlled by the HVECU 60, and a rotation speed sensor 112 such as a resolver.
Is supplied to the HVECU 60 from the motor rotation speed N _PM . The motor rotation speed N _PM corresponds to the pump rotation speed, that is, the discharge amount of the oil pump 108.

FIG. 8 is a circuit diagram for explaining a portion of the hydraulic circuit 24 that supplies a predetermined amount of lubricating oil to the heat generating portion of the belt type continuously variable transmission 12 to prevent overheating. The belt type continuously variable transmission 12 includes a vibration (runout) of the transmission belt 32, a change in shape between an arc portion wound around the variable pulleys 12a and 12b and a straight portion between the variable pulleys 12a and 12b, and the variable pulley 12a. , 12b, frictional contact between a large number of blocks 34 constituting the transmission belt 32, frictional contact between the block 34 and the variable pulleys 12a, 12b, hoop of the transmission belt 32, and the like. Friction contact between a large number of thin metal plates 38 that form 36 occurs, and heat generation is inevitable due to the frictional contact (sliding).
Since it is necessary to prevent overheating (such as seizure) by sprinkling lubricating oil on the second gear, etc., the belt type continuously variable transmission 12 is the power transmission mechanism to be lubricated in this embodiment.

In FIG. 8, the hydraulic oil (lubricating oil) pumped up by the oil pump 108 is adjusted to a predetermined line oil pressure P _L by the primary regulator valve 114, and the brake B1 and the clutch C1 are supplied from the oil supply passage 116. C2 is supplied to a hydraulic actuator such as a hydraulic cylinder of the belt type continuously variable transmission 12, and is used for switching the traveling mode, shifting control of the belt type continuously variable transmission 12, control of belt clamping pressure, and the like. The hydraulic oil flowing out to the flow rate adjusting oil passage 118 according to the pressure control of the primary regulator valve 114 is the secondary regulator valve 12.
By being pressure regulated based pressure P _B for a given belt lubricated by 0, is supplied to the belt-type continuously variable transmission 12 at a predetermined flow rate corresponding to the original pressure P _B through the orifice 122,
It is sprayed from a nozzle (not shown) and scattered on the transmission belt 32. The flow rate adjusting oil passage 118 corresponds to a flow rate adjusting section in which the flow of the lubricating oil to the belt type continuously variable transmission 12 side is restricted by the orifice 122, and the belt lubrication source pressure P _B is the duty of the exciting current by the HVECU 60. The linear solenoid valve 124 to be controlled controls the pressure so that the lubricating oil (operating oil) is supplied from the orifice 122 to the belt type continuously variable transmission 12 at a predetermined flow rate. These niria solenoid valve 124, secondary regulator valve 120, orifice 122, HVECU 6
0, the oil pump 108 and the like constitute the lubricating device of this embodiment. The hydraulic oil flowing out from the secondary regulator valve 120 to the drain oil passage 126 is used for lubrication of other parts, for example, lubrication of the friction plates and bearings of the clutches C1 and C2 and the brake B1, and part of the oil cooler. After being supplied to the oil pan 106 and cooled, it is returned to the oil pan 106.

The amount of heat generated by the belt type continuously variable transmission 12 is
The gear ratio γ, the input rotational speed Nin, the input torque Tin, the belt clamping pressure, and other operating conditions vary, and the transmission efficiency changes accordingly. On the other hand, the HVECU 60 determines that the minimum necessary hydraulic oil is required according to the transmission efficiency. As used for belt lubrication, it has a function of a lubricating oil supply amount control means for controlling the duty of the linear solenoid valve 124 and controlling the discharge amount of the oil pump 108.
FIG. 9 is a flowchart for specifically explaining the function of the lubricating oil supply amount control means for belt lubrication, which is repeatedly executed at a predetermined cycle time.

In step S1 of FIG. 9, the belt is calculated from a predetermined data map or an arithmetic expression using the gear ratio γ, the input rotational speed Nin, the input torque Tin, and the required hydraulic pressure Pd corresponding to the belt clamping pressure as parameters. The transmission efficiency η of the continuously variable transmission 12 is calculated. FIG. 10A is an example of a data map of the transmission efficiency η ₁ related to the gear ratio γ,
(b) is an example of a data map of the transmission efficiency η ₂ with respect to the input rotation speed Nin, (c) is an example of a data map of the transmission efficiency η ₃ with respect to the input torque Tin, and (d) is required to correspond to the belt clamping pressure. It is an example of a data map of the transmission efficiency η ₄ related to the hydraulic pressure Pd, which is obtained by experiments in advance and R
It is stored in a storage device such as an OM, and the total transmission efficiency η is obtained by multiplying these transmission efficiencies η ₁ , η ₂ , η ₃ , and η ₄ . HVECU60
The part that executes step S1 of the series of signal processing by means of functions as a transmission efficiency calculation means.

In step S2, the heat generation amount QH is calculated according to the following equation (1) using the input power (power) Pin, assuming that the energy loss of the transmission efficiency η has been completely taken away by heat generation due to friction. . The input power Pin is obtained by multiplying the input rotation speed Nin and the input torque Tin. Of the series of signal processing by the HVECU 60, the part that executes step S2 functions as a heat generation amount calculation means. QH = (1-η) × Pin ・ ・ ・ (1)

In step S3, the temperature difference (t ^* -) between the heat generation amount QH, the set target temperature t ^* and the oil temperature t _OIL of the hydraulic oil is set.
t _OIL ), the specific heat C _{OIL of the} hydraulic oil, and the heat exchange efficiency K for lowering the temperature of the transmission belt 32 due to the dispersion of the lubricating oil, the supply amount Q _OIL of the lubricating oil is calculated according to the following equation (2). The set target temperature t ^* is a target temperature of the transmission belt 32 which is predetermined in consideration of the durability of the transmission belt 32 and the oil temperature t *.
_OIL is the temperature of the hydraulic oil in the oil pan 106 before it is used for lubrication. When the temperature of the transmission belt 32 matches the set target temperature t ^* , the supply amount Q _OIL from the transmission belt 32 is used. The heat energy that can be taken and the calorific value QH match, and the transmission belt 32 sets the target temperature t ^*.
Maintained at. The temperature of the transmission belt 32 is the set target temperature t.
^When the temperature is lower than ^* , the actual temperature change of the hydraulic oil becomes smaller, so the supply amount Q _OIL becomes less than the heat generation amount QH, and the temperature of the transmission belt 32 rises while the temperature of the transmission belt 32 is set. If higher than the target temperature t ^* ,
Since the temperature change of the actual hydraulic oil becomes so large, the supply amount Q _OIL becomes excessive with respect to the heat generation amount QH, the temperature of the transmission belt 32 is lowered, and in any case, the set target temperature t ^* is finally reached. You can get closer. That is, equation (2) is
It is an arithmetic expression for calculating the supply amount Q _OIL according to the heat generation amount QH so that the temperature of the transmission belt 32 becomes the set target temperature t ^* . Of the series of signal processing by the HVECU 60, the part that executes step S3 functions as a supply amount calculation means. Q _OIL = QH / {K × (t ^* −t _OIL ) × C _OIL } (2)

In step S4, the discharge amount of the oil pump 108 is corrected according to the supply amount Q _OIL . The discharge amount of the oil pump 108 needs to be set according to the leakage amount, the lubricating flow rate, the cooler circulation flow rate, etc. of the hydraulic control circuit 24, and the oil temperature t _OIL and the line hydraulic pressure P _L which influence the leakage amount are used as parameters. In addition to being required, the amount of increase in the hydraulic fluid is corrected when the hydraulic oil is used, such as when the belt type continuously variable transmission 12 shifts or when the running mode is _switched . The sequential discharge amount is corrected by the electric motor 1 according to the corrected discharge amount.
The rotational speed N _{PM of} 10 is controlled. HVECU
Of the series of signal processing by 60, the part that executes step S4 functions as the ejection amount control means.

In step S5, the belt lubrication source pressure P _B is regulated so that the supply amount Q _OIL is supplied to the belt lubrication. The belt lubrication source pressure P _B is adjusted by the duty control of the linear solenoid valve 124, but the flow rate of the hydraulic oil passing through the orifice 122 is the oil temperature t.
_OIL, that is, because it changes depending on the viscosity of the hydraulic oil,
In the present embodiment, in addition to the supply amount Q _OIL, a belt lubrication source capable of supplying the operating oil by the supply amount Q _OIL through the orifice 122 based on a predetermined data map or arithmetic expression using the oil temperature t _OIL as a parameter. The pressure P _B is calculated, and the duty of the linear solenoid valve 124 is controlled according to the original pressure P _B for belt lubrication. HV
A portion of the series of signal processing by the ECU 60 that executes step S5 constitutes a flow rate adjusting means together with the linear solenoid valve 124, the secondary regulator valve 120, and the orifice 122.

As described above, in this embodiment, the energy loss amount of the transmission efficiency η of the belt type continuously variable transmission 12 is regarded as being converted into the heat energy by the heat generation due to the friction of the transmission belt 32 or the like, and the belt thereof is considered. Since the supply amount Q _OIL of the hydraulic oil for belt lubrication is controlled based on the transmission efficiency η that changes according to the operating state of the continuous variable transmission 12,
The belt lubrication can be appropriately controlled appropriately regardless of the amount of heat generation depending on the operating state, and the energy loss of the oil pump 108 due to the excessive supply of the lubricating oil is reduced to reduce the power consumption of the battery 42. As a result, fuel efficiency is finally improved.

Further, in this embodiment, the belt type continuously variable transmission 1 is used.
2 calculates the transmission efficiency η according to the operating state, calculates the heat generation amount QH based on the transmission efficiency η, calculates the temperature difference (t ^* -t) from the heat generation amount QH, the specific heat C _{OIL of the} hydraulic oil,
Based on the heat exchange efficiency K and the heat exchange efficiency K, the supply amount Q _OIL for belt lubrication is calculated according to the equation (2), and the supply amount Q _{OI L}
Since only the hydraulic oil is supplied to the transmission belt 32, the belt lubrication is performed so that the temperature of the transmission belt 32 reaches the set target temperature t ^* regardless of the operating state of the belt type continuously variable transmission 12, and the transmission belt 32 is cooled. Overheat is prevented and the supply amount Q _OIL is controlled to the necessary minimum.

Further, in this embodiment, the belt type continuously variable transmission 1 is used.
Since the transmission efficiency η is obtained using the gear ratio γ of 2, the input rotation speed Nin, the input torque Tin, and the belt clamping pressure (required oil pressure Pb) as parameters, the heat generation amount QH can be obtained with high accuracy. It is possible to control the supply amount of the hydraulic oil for belt lubrication with high accuracy according to the heat generation amount QH.

Further, in this embodiment, since the oil pump 108 is rotationally driven by the dedicated electric motor 110,
Energy loss due to excessive supply of lubricating oil is controlled by controlling the drive current of the electric motor 110 according to the required supply amount Q _OIL of the hydraulic oil for belt lubrication without affecting other driving forces such as vehicle driving force. Can be satisfactorily reduced.

Although the embodiment of the present invention has been described in detail with reference to the drawings, this is merely an embodiment,
The present invention can be implemented in various modified and improved modes based on the knowledge of those skilled in the art.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram illustrating a hybrid drive control device to which the present invention is applied.

FIG. 2 is a skeleton diagram showing a power transmission system of the hybrid drive control system of FIG.

FIG. 3 is a diagram illustrating a relationship between some running modes established in the hybrid drive control device in FIG. 1 and operating states of a clutch and a brake.

FIG. 4 is a perspective view illustrating a structure of a transmission belt of a belt type continuously variable transmission of the hybrid drive control device of FIG.

FIG. 5 is a diagram showing an example of a data map for calculating a target input rotation speed NINT using the vehicle speed V and the accelerator operation amount θac as parameters in the shift control of the belt type continuously variable transmission.

FIG. 6 is a diagram showing an example of a data map for obtaining a necessary hydraulic pressure Pd from an accelerator operation amount θac and a gear ratio γ in clamping pressure control of a belt type continuously variable transmission.

7 is a block diagram illustrating a schematic configuration of a hydraulic control circuit of the hybrid drive control device of FIG.

8 is a circuit diagram illustrating a circuit of a portion of the hydraulic control circuit of FIG. 7 that lubricates a transmission belt of a belt type continuously variable transmission.

FIG. 9 is a flowchart illustrating belt lubrication control for lubricating a transmission belt of a belt type continuously variable transmission.

FIG. 10 shows an example of a data map for obtaining transmission efficiencies η _{1 to} η ₄ in step S1 of FIG. 9 using the gear ratio γ, the input rotation speed Nin, the input torque Tin, and the required hydraulic pressure Pd (belt clamping pressure) as parameters. It is a figure.

[Explanation of symbols]

10: Hybrid drive control device 12: Belt type continuously variable transmission (power transmission mechanism) 32: Transmission belt (heat generation part) 60: HVECU 108: Oil pump
110: Electric motor 120: Secondary regulator valve 122: Orifice 124: Linear solenoid valve γ: Gear ratio Nin: Input rotation speed Tin: Input torque Pd: Required hydraulic pressure (belt clamping pressure) η, η ₁ , η ₂ , η ₃ , η ₄ : Transmission efficiency QH: Calorific value Q _OIL : Lubricant supply amount t ^* : Set target temperature
t _OIL : Oil temperature C _OIL : Specific heat Steps S1 to S5: Lubricating oil supply amount control unit Step S1: Transmission efficiency calculation unit Step S2: Heat generation amount calculation unit Step S3: Supply amount calculation unit Step S4: Discharge amount control unit Step S5 : Flow rate adjustment means

Front page continuation (51) Int.Cl. ⁷ identification code FI theme code (reference) F16N 7/38 F16N 7/38 C // F16H 59:72 F16H 59:72 (72) Inventor Hisonori Nomoto Toyota City, Aichi Prefecture Toyota Town No. 1 Toyota Motor Corporation F-term (reference) 3J050 AA03 CE03 CE07 DA01 3J063 AA02 AB22 AC04 BA20 CA01 XJ03 3J552 MA07 NA01 NB04 NB10 PA59 VA32Z VA37Z VA48W VA62W VC01Z VC06Z VD02Z

Claims (5)

[Claims] 1. A lubrication device for preventing overheating by supplying lubricating oil to a power transmission mechanism having a heat generating portion that generates heat according to an operating state by an oil pump to prevent overheating. A lubricating device for a power transmission mechanism, comprising a lubricating oil supply amount control means for controlling the supply amount of the lubricating oil in consideration of the changing transmission efficiency. 2. The lubricating oil supply amount control means includes a transmission efficiency calculation means for obtaining a transmission efficiency according to an operating state of the power transmission mechanism, and heat generation based on the transmission efficiency calculated by the transmission efficiency calculation means. A calorific value calculation means for calculating the amount, the calorific value calculated by the calorific value calculation means, a temperature difference between a preset target temperature and an actual oil temperature of the lubricating oil used for lubrication, and A supply amount calculating means for calculating the supply amount of the lubricating oil based on the specific heat of the lubricating oil, and a discharge amount for controlling the discharge amount of the oil pump in accordance with the supply amount obtained by the supply amount calculating means. The lubricating device for a power transmission mechanism according to claim 1, further comprising: control means. 3. The belt-type continuously variable transmission in which the power transmission mechanism has a transmission belt wound around a pair of variable pulleys whose groove width can be changed.
Lubricating device for power transmission mechanism according to. 4. The lubricating oil supply amount control means includes a gear ratio of the belt type continuously variable transmission, an input rotation speed of the belt type continuously variable transmission, an input torque of the belt type continuously variable transmission, and The lubrication device for a power transmission mechanism according to claim 3, wherein the transmission efficiency is obtained based on at least one of belt clamping pressures of the belt type continuously variable transmission. 5. The lubricating device for a power transmission mechanism according to claim 1, wherein the oil pump is rotationally driven by a dedicated electric motor.