JP2021076016A - vehicle - Google Patents

Abstract

To improve the accuracy in determining presence or absence of an abnormality in a hydraulic pressure supply path for generating clamping force of a winding member using an electric pump as a hydraulic pressure supply source to enhance the slip prevention effect of the winding member.SOLUTION: A vehicle according to the present invention includes an engine and a winding type continuously variable transmission, has an idling stop function of the engine, and includes a mechanical pump and an electric pump as pumps which are hydraulic supply sources of hydraulic oil for a hydraulic circuit of the continuously variable transmission and use the engine as a drive source. The vehicle includes a rotation speed sensor for detecting the rotation speed of the electric pump, a hydraulic sensor for detecting the oil pressure of hydraulic oil in the hydraulic circuit, and a control unit that performs first determination, which is abnormality determination on an actual rotation speed that is the rotation speed of the electric pump detected by the rotation speed sensor, and second determination, which is abnormality determination on an actual oil pressure that is the oil pressure detected by the hydraulic sensor, and that performs control to prohibit the idling stop function on the basis of determination results of the first determination and the second determination.SELECTED DRAWING: Figure 1

Description

The present invention includes an engine and a continuously variable transmission, has an idling stop function of the engine, and drives the engine as a pump that is a hydraulic supply source of hydraulic oil for the hydraulic circuit of the continuously variable transmission. It relates to a vehicle provided with a mechanical pump and an electric pump, and more particularly to a technique for preventing slipping of a winding member in a continuously variable transmission.

In a vehicle equipped with an engine, each component of the power transmission mechanism for transmitting power from the engine to the drive wheels is supplied from a mechanical pump (hereinafter referred to as "mechanical pump") operated by engine power. A configuration controlled by hydraulic pressure is known.

On the other hand, for the purpose of reducing fuel consumption (fuel consumption) and the like, vehicles capable of executing an idling stop function of stopping the engine regardless of the engine stop operation according to the establishment of predetermined conditions including the vehicle speed condition have become widespread. In such a vehicle, since the mechanical pump also stops when the engine is stopped while the idling stop function is being executed, a hydraulic supply source different from the mechanical pump for controlling the power transmission mechanism is required. Specifically, some vehicles with an idling stop function are equipped with a motor-driven electric pump that can supply flood control even when the engine is stopped.
For example, in the case of a vehicle equipped with a belt-type or chain-type continuously variable transmission, the clamping force of the winding member is generated by the flood control supplied from the electric pump during the execution of the idling stop function. Ru.

The following patent documents can be mentioned as related prior arts.

Japanese Patent No. 5437336 Japanese Patent No. 6277918 Japanese Unexamined Patent Publication No. 2009-133332 Japanese Patent No. 4226543

Here, in a vehicle equipped with a winding type continuously variable transmission, an electric pump is used as a hydraulic supply source as a hydraulic supply path for generating a clamping force (pinching pressure) of the winding member while the idling stop function is being executed. However, if an abnormality occurs in this oil supply path, the clamping force of the winding member may decrease due to the decrease in oil pressure, and the winding member may slip. There is.

Therefore, it is determined whether or not there is an abnormality in the oil supply path at the time of idling stop, and if an abnormality is found, the idling stop state is released (that is, the engine is started) to switch to the hydraulic supply by the mechanical pump. To be able to. This makes it possible to prevent the winding member from slipping.

At this time, in order to properly prevent the winding member from slipping, accuracy is required in determining the presence or absence of an abnormality in the hydraulic supply path. If the abnormality determination is not accurate, it is not possible to switch to the mechanical pump under appropriate conditions, and it is difficult to properly prevent the winding member from slipping.

The present invention has been made in view of the above problems, and is intended to improve the accuracy of determining the presence or absence of an abnormality in the hydraulic supply path for generating the clamping force of the winding member using the electric pump as the hydraulic supply source, and to perform the winding. The purpose is to enhance the anti-slip effect of the members.

The vehicle according to the present invention includes an engine and a winding type stepless transmission, has an idling stop function of the engine, and is a pump that is a hydraulic supply source of hydraulic oil for the hydraulic circuit of the stepless transmission. A vehicle equipped with a mechanical pump and an electric pump having the engine as a drive source, the rotation speed sensor for detecting the rotation speed of the electric pump and the oil pressure sensor for detecting the oil pressure of the hydraulic oil in the hydraulic circuit. In the first determination, which is an abnormality determination for the actual rotation speed, which is the rotation speed of the electric pump detected by the rotation speed sensor, and the abnormality determination for the actual oil pressure, which is the oil pressure detected by the oil pressure sensor. It is provided with a control unit that performs a certain second determination and controls to prohibit the idling stop function based on the determination results of the first determination and the second determination.

If the determination is made only based on the rotation speed of the electric pump, even if an abnormality occurs on the hydraulic circuit side, it may be overlooked. On the other hand, if it is determined whether or not there is an abnormality in the hydraulic pressure supply path for generating the clamping force, it can be considered that only the determination based on the hydraulic pressure needs to be performed. However, even if the flood pressure is normal, there may be a case where an abnormality has occurred in the electric pump. For example, it is conceivable that an abnormality on the hydraulic circuit side has occurred that cancels the hydraulic abnormality caused by the abnormality on the electric pump. In such a case, the abnormality on the electric pump side and the hydraulic circuit side happens to be the proper oil pressure. Is only occurring in the manner in which is obtained, and should not be determined to be normal. Therefore, in the present invention, not only the oil pressure but also the rotation speed of the electric pump is set as the target of the abnormality determination to improve the accuracy of the abnormality determination.

In the vehicle according to the present invention described above, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the control unit stops idling regardless of the determination result of the second determination. It is possible to configure the control to prohibit the function.
When there is an abnormality on the electric pump side, that is, on the oil pressure supply source side, it is difficult to correctly determine the abnormality in the hydraulic circuit by the second determination based on the detection information of the oil pressure. Therefore, when an abnormality on the electric pump side is determined by the first determination, the idling stop function is prohibited regardless of the result of the second determination.

In the vehicle according to the present invention described above, the control unit performs the first determination before the second determination, and when it is determined by the first determination that there is an abnormality in the actual rotation speed, the control unit performs the first determination. , It is possible to configure the control to prohibit the idling stop function without performing the second determination.
As a result, if it is determined by the first determination that there is an abnormality in the electric pump, the second determination is not performed.

In the vehicle according to the present invention described above, the control unit is information that identifies an abnormal portion from the electric pump and the hydraulic circuit based on the determination results of the first determination and the second determination. It is possible to configure the system to store information.
This makes it possible to store the information indicating the abnormal location in the vehicle as log information.

In the vehicle according to the present invention described above, when the control unit determines that there is an abnormality in the actual rotation speed by the first determination, it is regarded as an abnormal portion regardless of the determination result of the second determination. It is possible to have a configuration in which the storage process of the abnormal portion information in which only the electric pump is specified is performed.
When there is an abnormality on the electric pump side, that is, on the oil pressure supply source side, it is difficult to correctly determine the abnormality in the hydraulic circuit by the second determination based on the detected value of the oil pressure. Therefore, when an abnormality on the electric pump side is determined by the first determination, only the electric pump is stored for the abnormality location information specified as the abnormality location, and the result of the second determination is not referred to at that time. It is supposed to be.

According to the present invention, the slip prevention effect of the winding member in the winding type continuously variable transmission can be enhanced.

It is a figure which showed the structural outline of the vehicle as the embodiment which concerns on this invention. It is a schematic cross-sectional view of the continuously variable transmission in embodiment. It is a figure for demonstrating the structure of the hydraulic control part in an embodiment. It is a flowchart which showed the process for realizing the hydraulic pressure supply control as an embodiment. It is a flowchart which showed the process as another example of the hydraulic pressure supply control in an embodiment. It is explanatory drawing of the diagnosis rule of the abnormality part in embodiment. It is a flowchart which showed the process for storing the abnormal part information in an embodiment.

<1. Vehicle configuration overview ＞
FIG. 1 is a diagram showing an outline of the configuration of a vehicle 1 as an embodiment according to the present invention. In FIG. 1, only the configuration of the main part according to the present invention is extracted and shown from the configuration of the vehicle 1.
The vehicle 1 in the present embodiment includes an engine 2 as a traveling power source, a power transmission mechanism 3 having a torque converter 4, a forward / backward switching mechanism 5, and a continuously variable transmission 6, and a hydraulic pressure of hydraulic oil in the power transmission mechanism 3. It includes a hydraulic control unit 7 for control, a gear 8 and a gear 9, a differential gear 10, a drive wheel 11a and a drive wheel 11b, an engine control unit 12, a transmission mechanism control unit 13, and a bus 14. ..

The engine 2 is a traveling power source (motor) for traveling the vehicle 1, and consumes fuel to generate power to act on the drive wheels 11a and 11b of the vehicle 1. The engine 2 burns fuel to generate mechanical power (engine torque) on the crankshaft 2a, which is an engine output shaft, and the mechanical power can be output from the crankshaft 2a toward the drive wheels 11a and 11b. Has been done.

The power transmission mechanism 3 is provided in the power transmission path from the engine 2 to the drive wheels 11a and 11b, transmits power from the engine 2 to the drive wheels 11a and 11b, and is an oil as a liquid medium (hydraulic oil: However, it operates by the hydraulic pressure (which can also function as lubricating oil or cooling oil).
In the power transmission mechanism 3, the crankshaft 2a of the engine 2 and the input shaft Ps of the continuously variable transmission 6 are connected via a torque converter 4, a forward / backward switching mechanism 5, and the like, and the output shaft Ss of the continuously variable transmission mechanism 6 is connected. Is connected to the drive wheels 11a and 11b via the gear 8, the gear 9, the differential gear 10, and the like.

The torque converter 4 is arranged between the engine 2 and the forward / backward switching mechanism 5, and is configured to amplify (or maintain) the torque of the power transmitted from the engine 2 so that the torque converter 4 can be transmitted to the forward / backward switching mechanism 5. Has been done. The torque converter 4 includes a pump impeller 4a and a turbine runner 4b that are rotatably opposed to each other. The pump impeller 4a is integrally rotatably coupled to the crankshaft 2a via a front cover 4c, and the turbine runner 4b is switched forward and backward. It is configured by being connected to the mechanism 5. As the pump impeller 4a and the turbine runner 4b rotate, a viscous fluid such as hydraulic oil interposed between the pump impeller 4a and the turbine runner 4b circulates and flows, allowing a differential between the input and output. At the same time, it is possible to amplify and transmit the torque.

Further, the torque converter 4 further includes a lockup clutch 4d provided between the turbine runner 4b and the front cover 4c and rotatably connected to the turbine runner 4b. The lockup clutch 4d is operated by the pressure of the hydraulic oil supplied from the hydraulic control unit 7, and is switched between an engaged state (lockup ON) and an open state (lockup OFF) with the front cover 4c. When the lockup clutch 4d is engaged with the front cover 4c, the front cover 4c (that is, the pump impeller 4a) and the turbine runner 4b are engaged, and the relative rotation between the pump impeller 4a and the turbine runner 4b is restricted. Since the differential between the input and output is prohibited, the torque converter 4 transmits the torque transmitted from the engine 2 to the forward / backward switching mechanism 5 as it is.

The forward / backward switching mechanism 5 is configured to be able to shift the power (rotational output) from the engine 2 and to switch the rotation direction of the power (finally, the rotation direction of the drive wheels 11a and 11b). .. The forward / backward switching mechanism 5 includes a planetary gear mechanism 5a, a forward clutch (forward clutch) CL as a friction engaging element, a reverse brake (reverse brake) BR, and the like. The planetary gear mechanism 5a is a differential mechanism including a sun gear, a ring gear, a carrier, and the like as a plurality of rotating elements capable of differentially rotating each other. The forward clutch CL and the reverse brake BR are of the planetary gear mechanism 5a. It is an engaging element for switching the operating state, and can be configured by a friction type engaging mechanism such as a multi-plate clutch, and a hydraulic wet multi-plate clutch is used here.

In the forward / backward switching mechanism 5, the forward clutch CL and the reverse brake BR are operated by the pressure of the hydraulic oil supplied from the hydraulic control unit 7, and the operating state is switched. Specifically, the forward / backward switching mechanism 5 rotates the power from the engine 2 in the forward rotation (forward rotation) when the forward clutch CL is in the engaged state (engaged state: ON state) and the reverse brake BR is in the released state (OFF state). It is transmitted to the input shaft Ps in the direction in which the input shaft Ps rotates when the vehicle 1 moves forward. On the other hand, the forward / backward switching mechanism 5 reversely rotates the power from the engine 2 when the forward clutch CL is in the released state and the reverse brake BR is in the engaged state (the direction in which the input shaft Ps rotates when the vehicle 1 moves backward). ) Is transmitted to the input shaft Ps. In the forward / backward switching mechanism 5, both the forward clutch CL and the reverse brake BR are released in the neutral state.
Here, hereinafter, the control system that controls the engagement / disengagement of the forward clutch CL and the reverse brake BR as described above will be collectively referred to as "CB control system 5b".

The continuously variable transmission 6 is provided between the forward / backward switching mechanism 5 and the drive wheels 11a and 11b in the power transmission path from the engine 2 to the drive wheels 11a and 11b, and continuously transfers the power of the engine 2 (continuously). It is a transmission that can shift and output. Specifically, the stepless transmission 6 shifts the rotational power (rotational output) from the engine 2 transmitted (input) to the input shaft Ps at a predetermined gear ratio to the output shaft Ss which is the transmission output shaft. It transmits and outputs the power shifted from the output shaft Ss toward the drive wheels 11a and 11b.

The continuously variable transmission 6 includes a primary pulley 61 provided for the input shaft (primary shaft) Ps, a secondary pulley 64 provided for the output shaft (secondary shaft) Ss, and a primary pulley 61 and a secondary pulley 64. It is configured as a continuously variable transmission (CVT) that includes a winding member 67 such as a belt or chain that is hung (wound) between them. There is.

The primary pulley 61 coaxially opposes a primary side fixed sheave 62 whose position with respect to the input shaft Ps is fixed and rotates coaxially with the input shaft Ps and a primary side movable sheave 63 displaceable in the axial direction of the input shaft Ps. It is formed by arranging. Further, in the secondary pulley 64, the secondary side fixed sheave 65 whose position with respect to the output shaft Ss is fixed and rotates coaxially with the output shaft Ss and the secondary side movable sheave 66 which can be displaced in the axial direction of the output shaft Ss are coaxial. It is formed by arranging them facing each other. The winding member 67 has a substantially V-shaped groove (hereinafter referred to as “V groove”) formed between the fixed sheave 62 and the movable sheave 63 on the primary side and between the fixed sheave 65 and the movable sheave 66 on the secondary side. It is handed over to).

In the stepless transmission 6, the hydraulic pressure of the hydraulic oil supplied from the hydraulic control unit 7 to the hydraulic chamber of the primary pulley 61 (primary hydraulic chamber 68 described later) and the hydraulic chamber of the secondary pulley 64 (secondary hydraulic chamber 69 described later) (described later). A force (pinching pressure: clamping force) for the primary side movable sheave 63 and the secondary side movable sheave 66 to sandwich the winding member 67 between the primary side fixed sheave 62 and the secondary side fixed sheave 65 according to the primary pressure and the secondary pressure. ) Can be controlled. As a result, in each of the primary pulley 61 and the secondary pulley 64, the width of the V groove can be changed to adjust the rotation radius (winding diameter) of the winding member 67, which corresponds to the input rotation speed of the primary pulley 61. It is possible to steplessly change the gear ratio, which is the ratio of the input rotation speed (primary rotation speed) to the output shaft rotation speed (secondary rotation speed) corresponding to the output rotation speed of the secondary pulley 64. Further, by adjusting the pinching pressure of the winding member 67 of the primary pulley 61 and the secondary pulley 64, it is possible to transmit power with a torque capacity corresponding to the pinching pressure.

The specific configuration of the continuously variable transmission 6 in the present embodiment will be described later.

The power transmitted to the output shaft Ss of the continuously variable transmission 6 is transmitted to the differential gear 10 via the gears 8 and 9. The differential gear 10 transmits the transmitted power to the drive wheels 11a and 11b via the drive shafts. The differential gear 10 absorbs the difference in rotational speed between the drive wheels 11a and 11b that occurs when the vehicle 1 turns.

With the above configuration, in the vehicle 1, the power generated by the engine 2 is transmitted to the drive wheels 11a and 11b via the torque converter 4, the forward / backward switching mechanism 5, the continuously variable transmission 6, the differential gear 10, and the like. Can be done. As a result, the vehicle 1 can travel by generating a driving force [N] on the contact patch of the driving wheels 11a and 11b with the road surface.

The hydraulic control unit 7 uses the hydraulic oil of the hydraulic oil to lock up the torque converter 4, the forward clutch CL and the reverse brake BR of the forward / backward switching mechanism 5, the primary side movable sheave 63 and the secondary side movable sheave of the continuously variable transmission 6. It operates the power transmission mechanism 3 including 66 and the like.
The hydraulic control unit 7 includes a plurality of oil passages, an oil reservoir, an oil pump, a plurality of solenoid valves, and the like, and is supplied to each part of the power transmission mechanism 3 in response to a signal from the transmission mechanism control unit 13. Control the flow rate and oil pressure of hydraulic oil. The hydraulic control unit 7 also functions as a lubrication / cooling oil supply device that lubricates and cools a predetermined portion of the power transmission mechanism 3.

The engine control unit 12 and the transmission mechanism control unit 13 are configured to include a microcomputer having a CPU (Central Processing Unit), a ROM (Read Only Memory), a RAM (Random Access Memory), and the like, and are configured as a CAN (Controller Area Network). They are connected to each other so that they can communicate with each other via a bus 14 corresponding to a predetermined in-vehicle network communication standard such as.

The engine control unit 12 performs various operation controls such as fuel injection control, ignition control, and intake air amount adjustment control for the engine 2. Specifically, various operation controls for the engine 2 are performed by controlling various actuators provided in the engine 2 (for example, a throttle actuator for driving a throttle valve, an injector for injecting fuel, etc.).
The engine control unit 12 communicates with the transmission mechanism control unit 13, and outputs data regarding the operating state of the engine 2 to the transmission mechanism control unit 13 as needed. Further, if necessary, the operation of the engine 2 is controlled based on various signals from the transmission mechanism control unit 13.

The engine control unit 12 of the present embodiment is capable of executing an idling stop function of stopping the engine 2 regardless of the engine stop operation when a predetermined condition including a vehicle speed condition is satisfied. Here, the "idling stop" may be abbreviated as "IS" below.
Specifically, the engine control unit 12 of this example is operated under predetermined conditions defined as "operation permission conditions" of the IS function (for example, the engine 2 is sufficiently warmed up, all the doors are closed, and the operation is performed. It is determined whether or not the conditions (conditions such as the seat belt being worn) are satisfied. Then, under the condition that the operation permission condition is satisfied, the IS function is operated according to the predetermined condition defined as the "operation condition" of the IS function, that is, the predetermined condition including the vehicle speed condition. That is, the engine 2 is stopped (automatically) regardless of the engine stop operation.
In the case of this example, the vehicle speed condition is that the vehicle speed is equal to or less than a predetermined speed that can be regarded as a stopped state. As the operating conditions other than the vehicle speed, it is a condition that the brake pedal is depressed at least (other conditions such as the steering not being operated and not being a steep slope can be added).

The transmission mechanism control unit 13 controls the operation of each part of the power transmission mechanism 3 such as the torque converter 4, the forward / backward switching mechanism 5, and the continuously variable transmission 6 by controlling the hydraulic control unit 7. In particular, the gear ratio control of the continuously variable transmission 6 is performed.
The process as an embodiment executed by the transmission mechanism control unit 13 will be described later.

<2. Configuration of continuously variable transmission in the embodiment>
FIG. 2 is a schematic cross-sectional view of the continuously variable transmission 6.
In this example, the primary side fixed sheave 62 is integrally formed with the input shaft Ps, and the secondary side fixed sheave 65 is integrally formed with the output shaft Ss. The primary side movable sheave 63 is slidable on the input shaft Ps, and the secondary side movable sheave 66 is slidable on the secondary shaft Ss via a sliding guide such as a spline groove.

In the continuously variable transmission 6, a primary hydraulic chamber 68 is provided as a hydraulic chamber for applying flood control to the primary side movable sheave 63, and a secondary hydraulic chamber 69 is provided as a hydraulic chamber for applying flood pressure to the secondary side movable sheave 66. ing. In the figure, the hydraulic chamber wall of the primary hydraulic chamber 68 is shown as the hydraulic chamber wall W68, and the hydraulic chamber wall of the secondary hydraulic chamber 69 is shown as the hydraulic chamber wall W69.

The primary hydraulic chamber 68 is supplied with a hydraulic pressure as a primary pressure, and the secondary hydraulic chamber 69 is supplied with a hydraulic pressure as a secondary pressure. In gear ratio control, by adjusting the oil pressure so that the primary pressure gradually increases relative to the secondary pressure, the winding diameter on the primary side gradually increases and the gear ratio gradually decreases. (It will be on the High side). On the contrary, by adjusting the oil pressure so that the secondary pressure gradually increases relative to the primary pressure, the winding diameter on the primary side gradually decreases and the gear ratio gradually increases (LOW side). Will be).
FIG. 2 shows the state of the continuously variable transmission 6 when the gear ratio is substantially maximum.

<3. Configuration of flood control unit in the embodiment>
FIG. 3 is a diagram for explaining the configuration of the flood control unit 7. Note that FIG. 3 also shows the primary hydraulic chamber 68 and the secondary hydraulic chamber 69 formed in the continuously variable transmission 6 and the engine 2.

In FIG. 3, the hydraulic control unit 7 includes a mechanical pump 31 having an engine 2 as a drive source as an oil supply source for supplying oil to each unit of the power transmission mechanism 3. The mechanical pump 31 is, for example, an inscribed gear type pump such as a trochoid pump, a vane pump, or the like, and discharges hydraulic oil by rotating the rotor by the power of the engine 2.

When the engine 2 is operating and the mechanical pump 31 is in the driving state, the oil stored in the drain 32 in the hydraulic control unit 7 is sucked and discharged by the mechanical pump 31 via the strainer (filtration filter) 33. Will be done. The oil discharged from the mechanical pump 31 flows into the hydraulic path 34.

A line pressure adjusting valve 35 is provided in the hydraulic path 34. The line pressure adjusting valve 35 regulates the oil pressure generated by the mechanical pump 31. A control pressure (pilot pressure) is supplied to the line pressure adjusting valve 35 by the SLS linear solenoid 36. The SLS linear solenoid 36 is an electromagnetic valve that generates a control pressure according to a current value determined by a duty signal (duty value) transmitted from the transmission mechanism control unit 13 shown in FIG.

The line pressure adjusting valve 35 adjusts the flood pressure in the hydraulic path 34 according to the control pressure by the SLS linear solenoid 36. The flood pressure in the hydraulic path 34 adjusted by the line pressure adjusting valve 35 is used as the line pressure PL.

As the line pressure adjusting valve 35, for example, a spool valve in which the spool (valve body) slides in the axial direction of the spool (valve body) to open / close or switch the flow path can be applied, and the hydraulic path 34 can be applied to the input port. Is connected, and the SLS linear solenoid 36 is connected to the pilot port for inputting the pilot pressure, so that the excess flow generated by adjusting the line pressure PL can be discharged from the output port.

The hydraulic path 34 is a first oil passage 34a for supplying the oil pressure to the primary side (primary hydraulic chamber 68) of the continuously variable transmission 6 as an oil passage for supplying the oil pressure adjusted to the line pressure PL, and the secondary side (secondary side (primary hydraulic chamber 68). The third oil that supplies the oil to the second oil passage 34b that supplies the oil to the secondary hydraulic chamber 69) and the CB control system pressure regulating circuit 70 for adjusting the oil of the CB control system 5b shown in FIG. It has a road 34c.
The CB control system pressure adjusting circuit 70 includes a pressure adjusting valve, an actuator for controlling the operation of the pressure adjusting valve, and the like, and the actuator is driven and controlled by the transmission mechanism control unit 13 to adjust the oil pressure of the CB control system 5b. It is configured to do.

The CB control system pressure regulating circuit 70 is configured to engage / disengage the forward clutch CL and engage / disengage the reverse brake BR in the forward / backward switching mechanism 5 in order to supply the feed hydraulic pressure to the forward clutch CL. The clutch oil passage 71, which is the oil passage of the above, and the brake oil passage 72, which is an oil passage for supplying operating (engaging) hydraulic pressure to the reverse brake BR, are provided.

A first shift control valve 39 and a second shift control valve 40 are provided for the first oil passage 34a. The first shift control valve 39 is inserted between the primary oil passage and the first oil passage 34a communicated with the primary hydraulic chamber 68, and the duty is controlled by the transmission mechanism control unit 13. The first duty solenoid (DS1) 41 The oil supply to the primary oil passage, that is, the oil supply to the primary hydraulic chamber 68 is adjusted according to the drive of. Further, the second speed change control valve 40 is provided so that oil from the primary oil passage can be input, and the primary hydraulic chamber is driven by the drive of the second duty solenoid (DS2) 42 whose duty is controlled by the transmission mechanism control unit 13. Adjust the oil drain from 68. That is, when the first duty solenoid 41 is activated, oil is introduced into the primary hydraulic chamber 68 from the first shift control valve 39, and the primary side movable sheave 63 moves in the direction of narrowing the groove width of the primary pulley 61, resulting in this. , The winding diameter of the winding member 67 increases and upshifts. When the second duty solenoid 42 is activated, oil is discharged from the primary hydraulic chamber 68 by the second speed change control valve 40, the movable sheave 63 on the primary side moves in the direction of widening the groove width of the primary pulley 61, and the winding member 67 The winding diameter is reduced and downshifted. By operating the first duty solenoid 41 and the second duty solenoid 42 in this way, it is possible to control the gear ratio of the continuously variable transmission 6.

A pressure regulating valve 37 is provided for the second oil passage 34b. The pressure regulating valve 37 outputs the flood pressure regulated with the line pressure PL as the original pressure. Control pressure is supplied to the pressure adjusting valve 37 by the SLS linear solenoid 38. Similar to the SLS linear solenoid 36 of the line pressure adjusting valve 35, the SLS linear solenoid 38 is also an electromagnetic valve that generates a control pressure according to a current value determined by a duty signal (duty value) transmitted from the transmission mechanism control unit 13. It is configured as.

The pressure adjusting valve 37 is, for example, a spool valve, and the output oil pressure of the SLS linear solenoid 38 whose duty is controlled by the transmission mechanism control unit 13 is input as a pilot pressure, and the line pressure introduced into the valve based on the pilot pressure. The reduced pressure is output using PL as the original pressure. The oil pressure output from the pressure adjusting valve 37 is used as a secondary pressure and is supplied to the secondary hydraulic chamber 69 via the secondary oil passage. The pinching pressure of the winding member 67 in the continuously variable transmission 6 is increased or decreased according to the secondary pressure supplied in this way.

A sub pressure adjusting valve 43 is connected to the output port of the line pressure adjusting valve 35. The sub pressure adjusting valve 43 is also a spool valve like the line pressure adjusting valve 35, and is discharged from the line pressure adjusting valve 35 according to the control pressure of the SLS linear solenoid 44 whose duty is controlled by the transmission mechanism control unit 13. Adjust the oil pressure of the excess flow.

An L / U control system 46 that controls engagement / disengagement of the lockup clutch 4d of the torque converter 4 is further connected to the output port of the line pressure adjusting valve 35, and excess flow is generated from the line pressure adjusting valve 35. When this happens, the excess flow is regulated by the sub-pressure regulating valve 43, and the regulated excess flow is supplied to the L / U control system 46 (or a low-pressure control system that can be controlled at a lower pressure than the continuously variable transmission 6). To.

Further, the sub-pressure adjusting valve 43 is configured to be able to supply a further excess flow generated by adjusting the excess flow from the output port to lubrication of each part of a predetermined portion in the power transmission mechanism 3.
In the hydraulic control unit 7 of this example, a CVT lubricating oil passage 45, which is an oil passage for lubricating the continuously variable transmission 6, is provided as a configuration for lubricating each portion. Depending on the CVT lubricating oil passage 45, oil is supplied as lubricating oil to the winding member 67 of the continuously variable transmission 6.

In the flood control unit 7, an oil passage is formed so that the excess flow supplied to the L / U control system 46, lubrication of each part, and the like is finally returned to the drain 32.

Further, the hydraulic control unit 7 of this example is provided with an electric pump (EOP: Electrical Oil Pump) 50 driven by an electric motor. During idling stop, that is, when the operation of the mechanical pump 31 is stopped, the transmission mechanism control unit 13 drives the electric pump 50. The electric pump 50 includes a pump unit that discharges oil as the rotor rotates, and an electric motor that rotationally drives the rotor. The pump unit is composed of, for example, an inscribed gear pump such as a trochoid pump, a vane pump, or the like.

In the state where the electric pump 50 is driven, the oil stored in the drain 32 is sucked and discharged by the electric pump 50 via the strainer 33. The oil discharged from the electric pump unit 50 flows into the above-mentioned hydraulic path 34 via the check valve 52. That is, the oil discharge path of the electric pump 50 having the check valve 52 joins the oil discharge path of the mechanical pump 31.
In the state where the electric pump 50 is driven, the oil pressure generated by the electric pump 50 is regulated by the line pressure adjusting valve 35.

By providing the electric pump 50 as described above, even if the engine 2 is stopped by the idling stop function, the drive mechanism of the lockup clutch 4d and the continuously variable transmission 6 that use the electric pump 50 as a supply source can be locked. It is possible to supply to the hydraulic chamber and the like.

The hydraulic control unit 7 is provided with a rotation speed sensor 51 for detecting the rotation speed of the electric pump 50 and a line pressure sensor 53 for detecting the line pressure PL.
In this example, the rotation speed of the electric pump 50 detected by the rotation speed sensor 51 and the line pressure PL information detected by the line pressure sensor 53 are the "actual rotation speed" and "actual line pressure" information, respectively. Is supplied to the transmission mechanism control unit 13 (see FIG. 1).

<4. Hydraulic supply control as an embodiment>
As can be understood from the above description, in the vehicle 1 of the embodiment, when the engine 2 is stopped by the IS function, the electric pump 50 is driven by the transmission mechanism control unit 13 and the electric pump 50 is used as a supply source. The winding member 67 is clamped by the hydraulic pressure. As a result, slip prevention of the winding member 67 can be achieved.

In the present embodiment, in the case where the electric pump 50 is driven while the engine is stopped by the IS function to form a hydraulic supply path using the electric pump 50 as the oil supply source, the winding member 67 is adopted. The transmission mechanism control unit 13 executes the following processing in order to enhance the anti-slip effect of the above.

FIG. 4 is a flowchart showing a specific processing procedure executed by the transmission mechanism control unit 13 in order to realize the hydraulic supply control as the embodiment. The transmission mechanism control unit 13 executes the process shown in FIG. 4 based on a program stored in a predetermined storage device such as a built-in ROM.
The transmission mechanism control unit 13 repeatedly executes the process shown in FIG. 4 while the IS function is being executed (that is, while the electric pump 50 is being driven). For example, it is repeatedly executed at a predetermined cycle.

In FIG. 4, the transmission mechanism control unit 13 executes the first determination process in step S101. The first determination is an abnormality determination regarding the actual rotation speed of the electric pump 50. Specifically, as the first determination, it is determined whether or not the actual rotation speed is within a predetermined range as the normal range. In this example, the first determination is whether or not the difference between the actual rotation speed and the predetermined reference value is within the predetermined value. At this time, as the reference value, the target value of the rotation speed used for driving the electric pump 50 (hereinafter referred to as “target value Tr”) is used. That is, as the first determination in this case, the transmission mechanism control unit 13 calculates the difference between the actual rotation speed value acquired from the rotation speed sensor 51 and the target value Tr, and the value of the difference falls within a predetermined value. Judge whether or not.

In step S102 following step S101, the transmission mechanism control unit 13 performs the second determination process. The second determination is an abnormality determination regarding the actual line pressure detected by the line pressure sensor 53. As the second determination, it is determined whether or not the actual line pressure is within the predetermined range as the normal range. In this example, the difference between the actual line pressure and the predetermined reference value is within the predetermined value. It is performed as a judgment as to whether or not it fits. At this time, as the reference value, the value of the line pressure PL estimated from the rotation speed of the electric pump 50 (hereinafter referred to as “assumed line pressure Spl”) is used. Specifically, the value of the line pressure PL estimated from the rotation speed as the target value Tr described above is used as the reference value. As the second determination in this case, the difference between the actual line pressure value acquired from the line pressure sensor 53 and the assumed line pressure Spl is calculated, and it is determined whether or not the difference value is within a predetermined value. ..

In step S103 following step S102, the transmission mechanism control unit 13 determines whether or not the EOP is abnormal. That is, based on the result of the first determination in step S101, it is determined whether or not an abnormality is found in the electric pump 50. Specifically, in this example, it is determined whether or not the determination result that the difference between the actual rotation speed and the target value Tr is not within the predetermined value is obtained in the first determination in step S101.

When the difference between the actual rotation speed and the target value Tr is within a predetermined value and it is determined that there is no EOP abnormality, the transmission mechanism control unit 13 proceeds to step S104 and determines whether or not the hydraulic circuit is abnormal. That is, based on the result of the second determination in step S102, it is determined whether or not an abnormality is found in the actual line pressure. Specifically, in this example, it is determined whether or not the determination result that the difference between the actual line pressure and the assumed line pressure Spl is not within the predetermined value is obtained in the second determination in step S102.
Here, in the case where an abnormality is found in the actual line pressure in the hydraulic supply path for generating the clamping force of the winding member 67 even though there is no abnormality in the electric pump 50 as the hydraulic supply source, the case is described. It can be presumed that the cause of the abnormality is on the hydraulic circuit side in the subsequent stage of the electric pump 50 in the hydraulic supply path. Therefore, the determination process in step S104 functions as a process for determining the presence or absence of an abnormality in the hydraulic circuit.

For confirmation, the "hydraulic circuit" referred to in the present specification means a part in the hydraulic supply path for supplying hydraulic pressure to a predetermined hydraulic supply target, which is later than the hydraulic supply source. To do.
There are various possible causes for the abnormality on the hydraulic circuit side. For example, a failure of the line pressure adjusting valve 35 or the SLS linear solenoid 36, a failure of the line pressure sensor 53, or the like can be considered.

If it is determined in step S104 that the hydraulic circuit is not abnormal, the transmission mechanism control unit 13 ends a series of processes shown in FIG. That is, when neither the EOP abnormality nor the hydraulic circuit abnormality occurs, the driving state of the electric pump 50 is continued.

The transmission mechanism control unit 13 proceeds to step S105 and executes IS prohibition processing in each of the case where it is determined in step S103 that the EOP is abnormal and the case where it is determined in step S104 that the hydraulic circuit is abnormal. .. That is, information instructing the prohibition of the IS function is given to the engine control unit 12. At the same time, the transmission mechanism control unit 13 stops driving the electric pump 50.

In response to the instruction to prohibit the IS function, the engine control unit 12 releases the engine stopped state by the IS function. That is, the engine 2 is restarted. As a result, the driving of the mechanical pump 31 is started, and the state is switched to the hydraulic supply state using the mechanical pump 31 as a supply source.

In response to the execution of the process of step S105, the transmission mechanism control unit 13 ends a series of processes shown in FIG.

Here, as can be seen with reference to FIG. 4, in the present embodiment, the abnormality determination (first determination) regarding the actual rotation speed of the electric pump 50 and the abnormality determination (second determination) regarding the actual line pressure in the hydraulic circuit ) Is used as the basis for the IS prohibition process.
When determining the presence or absence of an abnormality in the hydraulic supply path for generating the clamping force of the winding member 67, it is conceivable to perform only the determination based on the actual rotation speed of the electric pump 50. However, in that case, even if an abnormality occurs on the hydraulic circuit side, it may be overlooked. On the other hand, if it is determined whether or not there is an abnormality in the hydraulic pressure supply path for generating the clamping force, it can be considered that only the determination based on the hydraulic pressure needs to be performed. However, even if the oil pressure is normal, there may be a case where an abnormality has occurred in the electric pump 50. For example, it is conceivable that an abnormality on the hydraulic circuit side has occurred that cancels the hydraulic abnormality caused by the abnormality on the electric pump 50. In such a case, an abnormality on the electric pump 50 side and the hydraulic circuit side happens to occur. This is a case where it only occurs in a manner in which proper oil pressure can be obtained and should not be determined to be normal. Therefore, in the present embodiment, not only the oil pressure but also the rotation speed of the electric pump 50 is targeted for the abnormality determination, so that the accuracy of the abnormality determination is improved.
As a result, it is possible to release the engine stopped state by the IS function based on an appropriate abnormality determination result, and it is possible to enhance the anti-slip effect of the winding member 67.

Further, as can be seen with reference to FIG. 4, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the transmission mechanism control unit 13 stops idling regardless of the determination result of the second determination. Control is performed to prohibit the function.
When there is an abnormality on the electric pump 50 side, that is, on the oil pressure supply source side, it is difficult to correctly determine the abnormality in the hydraulic circuit by the second determination based on the detection information of the oil pressure. Therefore, when an abnormality on the electric pump 50 side is determined by the first determination, the idling stop function is prohibited regardless of the result of the second determination.
As a result, the efficiency of the abnormality determination process can be improved.

<5. Another example of hydraulic supply control>
FIG. 5 is a flowchart showing a process as another example of the hydraulic supply control. As in the case of FIG. 4, the execution subject of the process is the transmission mechanism control unit 13, and the process of FIG. 5 is also repeatedly executed during the execution of the IS function.
In the following description, the same step numbers will be assigned to the processes that are the same as the processes that have already been explained, and the description will be omitted.

In this case, the transmission mechanism control unit 13 determines in step S103 whether or not the EOP is abnormal, in response to the process of the first determination being performed in step S101.
Then, if it is not an EOP abnormality, the process proceeds to step S102 to perform the second determination process, and then in step S104, it is determined whether or not the hydraulic circuit is abnormal.
When it is determined in step S104 that the hydraulic circuit is not abnormal, the transmission mechanism control unit 13 ends a series of processes shown in FIG.

Also in this case, when it is determined in step S103 that the EOP is abnormal, and in each case where it is determined in step S104 that the hydraulic circuit is abnormal, the transmission mechanism control unit 13 proceeds to step S105 to perform IS prohibition processing. Execute.

By the process of FIG. 5 as described above, the transmission mechanism control unit 13 makes the first determination before the second determination, and when it is determined by the first determination that there is an abnormality in the actual rotation speed, the first determination is performed. (Ii) Control is performed to prohibit the idling stop function without making a judgment.
As described above, when there is an abnormality on the electric pump 50 side, it becomes difficult to correctly determine the abnormality of the hydraulic circuit by the second determination. Therefore, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the second determination is not performed.
As a result, it is possible to reduce the processing load related to the abnormality determination.

<6. Diagnosis of abnormal parts ＞
In the vehicle 1 of the present embodiment, information representing the diagnosis result of the abnormal portion is stored based on the determination results of the first determination and the second determination. Specifically, the transmission mechanism control unit 13 performs storage processing of abnormal portion information, which is information that identifies an abnormal portion from the electric pump 50 and the hydraulic circuit, based on the determination results of the first determination and the second determination.

FIG. 6 shows the correspondence between the combination of the determination results of the first determination and the second determination and the diagnosis result of the abnormal portion as an explanatory diagram of the diagnosis rule of the abnormal portion.
If the determination results of the first and second determinations both represent normal, the diagnosis result is that both the electric pump 50 and the hydraulic circuit are normal. When the result of the first determination is normal and the result of the second determination is abnormal, the diagnosis result is that the electric pump 50 is normal and the hydraulic circuit is abnormal.
When the judgment result of the first judgment represents an abnormality, regardless of whether the result of the second judgment represents normal or abnormal, only the electric pump 50 is diagnosed as abnormal. .. As described above, when there is an abnormality on the electric pump 50 side as the oil supply source, it is difficult to correctly determine the abnormality on the hydraulic circuit side in the subsequent stage. Therefore, only the electric pump 50 is left with the diagnosis result of abnormality.

The flowchart of FIG. 7 illustrates a procedure of processing executed by the transmission mechanism control unit 13 for storing abnormal location information according to the above diagnostic rule.
As shown in the drawing, the transmission mechanism control unit 13 performs the first determination process in step S101, and then determines whether or not the EOP is abnormal in step S103.

If the EOP is not abnormal, the transmission mechanism control unit 13 performs the second determination process in step S102, and then determines whether or not the hydraulic circuit is abnormal in step S104. If the hydraulic circuit is not abnormal, the transmission mechanism control unit 13 ends a series of processes shown in FIG. 7. That is, if no abnormality is found in either the electric pump 50 or the hydraulic circuit, the abnormality location information is not stored.

When it is determined in step S104 that the hydraulic circuit is abnormal, the transmission mechanism control unit 13 executes the IS prohibition process in step S105, and then performs the storage process of the hydraulic circuit abnormality information in step S201, which is shown in FIG. Finish a series of processing.
In the storage process of step S201, the transmission mechanism control unit 13 performs a process of storing information that identifies only the hydraulic circuit as an abnormal location in a predetermined non-volatile memory (not shown) as the abnormal location information.

On the other hand, when the transmission mechanism control unit 13 determines in step S103 that the EOP abnormality is present, the transmission mechanism control unit 13 performs the IS prohibition process in step S105 and then executes the storage process of the EOP abnormality information in step S202. The series of processes shown in 7 is completed. In the storage process of step S202, the transmission mechanism control unit 13 performs a process of storing the information specifying that the abnormal location is only the electric pump 50 in the above-mentioned non-volatile memory as the abnormal location information.

In the process shown in FIG. 7, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the abnormality location information in which only the electric pump 50 is specified as the abnormality location regardless of the determination result of the second determination. Is stored.
As a result, when it is determined in the first determination that there is an abnormality in the actual rotation speed, the second determination can be omitted, and the determination process required for diagnosing the abnormal portion can be efficiently reduced.

In the above, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the abnormality location information in which only the electric pump 50 is specified as the abnormality location is stored regardless of the determination result of the second determination. However, it is also possible to store the abnormal location information in which both the electric pump 50 and the hydraulic circuit are identified as abnormal locations, instead of the abnormal location information in which only the electric pump 50 is specified.
As a result, when repairing the vehicle 1, not only the electric pump 50 side but also the hydraulic circuit side can be inspected, and when there is an abnormality not only in the electric pump 50 but also in the hydraulic circuit side, the flood control It is possible to reduce the possibility that an abnormality on the circuit side is overlooked.

<7. Modification example>
In the above, an example of performing an abnormality determination targeting the line pressure PL has been given as the second determination, but as the second determination, an abnormality determination targeting the oil pressure in the hydraulic circuit may be performed. Specifically, the electric pump 50 may be used as the oil supply source, and the oil pressure at an arbitrary position in the oil pressure supply path that generates the clamping force of the winding member 67 may be targeted. For example, the above-mentioned abnormality determination can be made for the secondary pressure. In that case, a hydraulic sensor for detecting the secondary pressure is provided, and the detection information of the hydraulic sensor is input to the transmission mechanism control unit 13. Should be taken.

Further, in the above, an example is given in which the abnormality determination by the first determination and the second determination and the IS prohibition process based on the result of the abnormality determination are performed during the execution of the IS function, but these processes are performed by the IS function. It is not limited to what you do during execution.
For example, the first determination and the second determination are performed in a state where the electric pump 50 is driven after the vehicle control system is started (for example, after the start instruction is given by the start switch provided on the vehicle 1) and before the engine 2 is started. It is possible to do it. As a result, the IS function can be prohibited before the execution condition of the IS function is satisfied. That is, it is possible to prevent the winding member 67 from slipping due to the flood control being supplied by the electric pump 50 in a state where the electric pump 50 or the hydraulic circuit has an abnormality.
Alternatively, the first determination and the second determination may be performed while the engine is stopped after the vehicle control system is instructed to stop (instruction by the operation of the occupant) until the occupant disembarks. As a result, when there is an abnormality in the electric pump 50 or the hydraulic circuit, the IS function can be disabled at the next boarding, and it is possible to prevent the winding member 67 from slipping. it can.

<8. Summary of embodiments>
As described above, the vehicle (1) of the embodiment includes an engine (2) and a winding type stepless transmission (6), has an idling stop function of the engine, and is a stepless transmission. A vehicle equipped with a mechanical pump (31) and an electric pump (50) whose drive source is an engine as a pump that is a hydraulic supply source of hydraulic oil for a hydraulic circuit, and rotates to detect the rotation speed of the electric pump. Abnormality determination of the actual rotation speed, which is the rotation speed of the electric pump detected by the number sensor (51), the oil pressure sensor (line pressure sensor 53) that detects the oil pressure of the hydraulic oil in the hydraulic circuit, and the rotation speed sensor. A certain first judgment and a second judgment which is an abnormality judgment about the actual oil pressure (actual line pressure) which is the oil pressure detected by the oil pressure sensor are performed, and idling is performed based on the judgment results of the first judgment and the second judgment. It includes a control unit (transmission mechanism control unit 13) that controls to prohibit the stop function.

If the determination is made only based on the rotation speed of the electric pump, even if an abnormality occurs on the hydraulic circuit side, it may be overlooked. On the other hand, if it is determined whether or not there is an abnormality in the hydraulic pressure supply path for generating the clamping force, it can be considered that only the determination based on the hydraulic pressure needs to be performed. However, even if the flood pressure is normal, there may be a case where an abnormality has occurred in the electric pump. For example, it is conceivable that an abnormality on the hydraulic circuit side has occurred that cancels the hydraulic abnormality caused by the abnormality on the electric pump. In such a case, the abnormality on the electric pump side and the hydraulic circuit side happens to be the proper oil pressure. Is only occurring in the manner in which is obtained, and should not be determined to be normal. Therefore, in the present invention, not only the oil pressure but also the rotation speed of the electric pump is set as the target of the abnormality determination to improve the accuracy of the abnormality determination.
Therefore, based on an appropriate abnormality determination result, it is possible to prevent the engine from being stopped by the idling stop function, and it is possible to enhance the slip prevention effect of the winding member in the continuously variable transmission.

Further, in the vehicle of the embodiment, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the control unit controls to prohibit the idling stop function regardless of the determination result of the second determination. Is going.
When there is an abnormality on the electric pump side, that is, the oil pressure supply source side, it is difficult to correctly determine the abnormality of the hydraulic circuit by the second determination based on the detection information of the oil pressure. Therefore, when an abnormality on the electric pump side is determined by the first determination, the idling stop function is prohibited regardless of the result of the second determination.
As a result, the efficiency of the abnormality determination process can be improved.

Further, in the vehicle of the embodiment, the control unit makes the first determination before the second determination, and when it is determined by the first determination that there is an abnormality in the actual rotation speed, the second determination is performed. Control is performed to prohibit the idling stop function without using it.
As a result, if it is determined by the first determination that there is an abnormality in the electric pump, the second determination is not performed.
Therefore, it is possible to reduce the processing load related to the abnormality determination.

Furthermore, in the vehicle of the embodiment, the control unit performs a storage process of abnormal location information, which is information identifying an abnormal location from the electric pump and the hydraulic circuit, based on the determination results of the first determination and the second determination. Is going.
This makes it possible to store the information indicating the abnormal location in the vehicle as log information.
Therefore, the maintainability of the vehicle can be improved.

Further, in the vehicle of the embodiment, when it is determined by the first determination that there is an abnormality in the actual rotation speed, the control unit identifies only the electric pump as an abnormal portion regardless of the determination result of the second determination. The stored abnormal location information is being processed.
When there is an abnormality on the electric pump side, that is, the oil pressure supply source side, it is difficult to correctly determine the abnormality of the hydraulic circuit by the second determination based on the detected value of the oil pressure. Therefore, when an abnormality on the electric pump side is determined by the first determination, only the electric pump is stored for the abnormality location information specified as the abnormality location, and the result of the second determination is not referred to at that time. It is supposed to be.
As a result, it is possible to improve the efficiency of diagnosing the abnormal part.

1 Vehicle 2 Engine 2a Crankshaft 3 Power transmission mechanism Ps Input shaft Ss Output shaft 6 Stepless transmission 61 Primary pulley 62 Primary side fixed sheave 63 Primary side movable sheave 64 Secondary pulley 65 Secondary side fixed sheave 66 Secondary side movable sheave 67 winding Hanging member 7 Hydraulic control unit 12 Engine control unit 13 Transmission mechanism control unit 68 Primary hydraulic chamber 69 Secondary hydraulic chamber 50 Electric pump 51 Rotation speed sensor 52 Check valve 53 Line pressure sensor 31 Mechanical pump 34 Hydraulic path 34a First oil passage 34b 2nd oil passage 34c 3rd oil passage 35 Line pressure adjustment valve 36, 38, 44 SLS linear solenoid PL line pressure

Claims (5)

It is equipped with an engine and a continuously variable transmission, has an idling stop function of the engine, and uses the engine as a drive source as a pump that is a hydraulic supply source of hydraulic oil for the hydraulic circuit of the continuously variable transmission. It is a vehicle equipped with a mechanical pump and an electric pump.
A rotation speed sensor that detects the rotation speed of the electric pump and
A hydraulic sensor that detects the hydraulic pressure of the hydraulic oil in the hydraulic circuit, and
The first determination, which is an abnormality determination regarding the actual rotation speed, which is the rotation speed of the electric pump detected by the rotation speed sensor, and the second determination, which is an abnormality determination regarding the actual oil pressure which is the oil pressure detected by the oil pressure sensor. A vehicle including a control unit that performs two determinations and controls to prohibit the idling stop function based on the determination results of the first determination and the second determination. The control unit
The vehicle according to claim 1, wherein when it is determined by the first determination that there is an abnormality in the actual rotation speed, control is performed to prohibit the idling stop function regardless of the determination result of the second determination. The control unit
If the first determination is performed before the second determination and it is determined by the first determination that there is an abnormality in the actual rotation speed, the idling stop function is prohibited without performing the second determination. The vehicle according to claim 1 or 2, which controls the vehicle. The control unit
Any of claims 1 to 3, which stores the abnormal location information which is the information for identifying the abnormal location from the electric pump and the hydraulic circuit based on the determination results of the first determination and the second determination. Vehicles listed in Crab. The control unit
When it is determined by the first determination that there is an abnormality in the actual rotation speed, the storage process of the abnormality location information in which only the electric pump is specified as the abnormality location is performed regardless of the determination result of the second determination. The vehicle according to claim 4.

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