JP6546816B2 - Pump system and control method of pump system - Google Patents

Description

  The present invention relates to a pump system and a control method of the pump system.

  According to Patent Document 1, power is transmitted from the drive wheels to the oil pump to drive the oil pump during inertia running control, that is, when inertia running is performed by automatically stopping the traveling drive source during vehicle running. Technology is disclosed. Patent Document 1 further discloses that, when the vehicle speed is equal to or less than a predetermined vehicle speed, the oil pump is driven by the electric motor.

Patent No. 5035468

  In the inertia running control, fuel consumption can be improved by performing the inertia running while stopping the driving source for running. However, when the oil pump is driven by the power from the drive wheels during inertia running control, kinetic energy of the vehicle is consumed by the work of the oil pump. As a result, the dispersive travel distance becomes short, and the fuel efficiency improvement effect may be impaired.

  The present invention has been made in view of such technical problems, and a pump system and a pump system capable of improving the fuel efficiency when the oil pump is driven by the power from the driving wheel during the inertia running control. The purpose is to provide a control method for

A pump system according to an aspect of the present invention includes an oil pump driven by a traveling drive source of a vehicle to discharge oil, a motor provided to drive the oil pump, and a power transmission device to the oil pump And a first power transmission device for blocking power transmission and power transmission from the traveling drive source to the oil pump, and blocking power transmission and power transmission from a drive wheel of the vehicle to the oil pump Automatically stopping the traveling drive source during traveling of the vehicle, including: a second power transmission device to perform, and a third power transmission device to shut off power transmission and power transmission from the motor to the oil pump A power transmission device for transmitting power from the drive wheel to the oil pump by the second power transmission device during inertial traveling control in which inertial traveling is performed by The motor is driven when the state quantity indicating the charge state of the battery for supplying power to the motor is larger than the first predetermined amount during the row control, and the power transmission device is driven by the third power transmission device. A control unit for performing power transmission from a motor to the oil pump, and a transmission ratio control unit for controlling a transmission ratio of a variator provided in a power transmission path for transmitting power from the traveling drive source to the drive wheel; Equipped with The second power transmission device is provided to interrupt power transmission and power transmission from the drive wheel to the oil pump via the variator. The power transmission device is provided in the second power transmission device and the third power transmission device, and power from the drive wheel via the variator is input to one of the fastening elements, and the other of the other fastening elements is provided. It further includes a clutch to which the power of the motor is input. The clutch causes the second power transmission device to transmit power from the drive wheel to the oil pump when the rotational speed of the one fastening element is higher than the rotational speed of the other fastening element. When the rotational speed of the other fastening element is higher than the rotational speed of the one fastening element, power transmission from the motor to the oil pump is performed by the third power transmission device. When driving the motor, the control unit controls the motor such that the rotational speed of the other fastening element is higher than the rotational speed of the one fastening element. The transmission ratio control unit controls the transmission ratio of the variator such that the input side rotational speed of the variator becomes a second predetermined rotational speed lower than a first predetermined rotational speed during the inertial traveling control. The first predetermined rotation speed and the second predetermined rotation speed control the gear ratio of the variator within the gear ratio range larger than the minimum gear ratio and smaller than the maximum gear ratio according to the vehicle speed during the inertial traveling control It is an input side rotational speed of the said variator set when carrying out.

According to another aspect of the present invention, an oil pump driven by a traveling drive source of a vehicle to discharge oil, a motor provided to drive the oil pump, and a power transmission device to the oil pump And a first power transmission device for blocking power transmission and power transmission from the traveling drive source to the oil pump, and blocking power transmission and power transmission from a drive wheel of the vehicle to the oil pump Automatically stopping the traveling drive source during traveling of the vehicle, including: a second power transmission device to perform, and a third power transmission device to shut off power transmission and power transmission from the motor to the oil pump in the coasting control in performing coasting, the power transmission unit by the second power transmission device transmits power to the oil pump from the drive wheel, or the traveling drive source And a variator provided on a power transmission path for transmitting power to the driving wheel, the second power transmission device, disconnected from the drive wheel through the variator of power transmission and power transmission to the oil pump The power transmission apparatus is provided to the second power transmission apparatus and the third power transmission apparatus, and power from the drive wheel is input to one of the fastening elements via the variator. , The other fastening element further includes a clutch into which the power of the motor is inputted, and the clutch is configured to move the second fastening element when the rotational speed of the one fastening element is higher than the rotational speed of the other fastening element. Power is transmitted from the drive wheel to the oil pump by a power transmission device, and the rotational speed of the other fastening element is the rotational speed of the one fastening element If remote high, a control method for controlling a pumping system to perform power transmission to the oil pump from the motor by the third power transmission device, during the coasting control, power to the motor Driving the motor such that the rotational speed of the other fastening element is higher than the rotational speed of the one fastening element when the state quantity indicating the charge state of the battery for supplying Causing the power transmission device to transmit power from the motor to the oil pump by the third power transmission device, and the input-side rotational speed of the variator during the inertial travel control being greater than a first predetermined rotational speed low and the second to control the speed ratio of the variator to a predetermined rotational speed, only contains the first predetermined rotational speed and the second predetermined rotational speed, the inertia Pump system for setting the input side rotational speed of the variator, which is set when controlling the transmission ratio of the variator within the transmission ratio range larger than the minimum transmission ratio and smaller than the maximum transmission ratio according to the vehicle speed during traveling control A control method is provided.

  According to these aspects, when the battery has a margin, the kinetic energy of the vehicle can be prevented from being consumed by the oil pump by driving the oil pump by the motor during the inertia running control. Therefore, when the oil pump is driven by the power from the drive wheels during inertia running control, fuel efficiency can be improved by improving the inertia running distance.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic block diagram of the vehicle carrying the pump system of embodiment. It is a figure showing an example of control of an embodiment with a flow chart. It is a figure showing an example of a shift map. It is a figure which shows an example of the timing chart corresponding to control of embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the attached drawings. The transmission gear ratio of the variator is a value obtained by dividing the input rotational speed by the output rotational speed, and is referred to as Low when the transmission ratio is large and High when the transmission ratio is small.

  FIG. 1 is a schematic configuration diagram of a vehicle 1. The vehicle 1 includes an engine 2, a torque converter 3, a motor generator 4, a pump 5, a first one-way clutch 6, a forward / reverse switching mechanism 7, a variator 8, a second one-way clutch 9, and a final reduction mechanism. 10, a drive wheel 11, and a hydraulic circuit 100.

  The engine 2 constitutes a drive source of the vehicle 1 and the pump 5. The output of the engine 2 is transmitted to the drive wheel 11 via the torque converter 3, the first one-way clutch 6, the forward / reverse switching mechanism 7, the variator 8, and the final reduction gear mechanism 10. In other words, the torque converter 3, the first one-way clutch 6, the forward / reverse switching mechanism 7, the variator 8 and the final reduction gear mechanism 10 are provided in a power transmission path for transmitting power from the engine 2 to the drive wheels 11.

  The torque converter 3 transmits power via fluid. In the torque converter 3, the power transmission efficiency can be enhanced by engaging the lockup clutch.

  The motor generator 4 constitutes a drive source of the pump 5. Hereinafter, motor generator 4 is referred to as M / G 4. The inverter 41 is provided in M / G4. The M / G 4 is driven by the power output from the inverter 41. A battery 42 is connected to the inverter 41. Energy regenerated by the M / G 4 as electric power when the vehicle 1 is braked is supplied to the battery 42 via the inverter 41. The M / G 4 is configured by, for example, a synchronous electric rotating machine driven by three-phase alternating current.

  The pump 5 is driven when power is transmitted from at least one of the engine 2, the M / G 4, and the primary pulley 81 (drive wheel 11), and discharges oil.

  The first one-way clutch 6 is provided between the engine 2 and the variator 8, specifically, between the torque converter 3 and the forward / reverse switching mechanism 7. The first one-way clutch 6 includes a first inner ring 61, a first outer ring 62, and a first clutch portion 63. Further, the first one-way clutch 6 is provided with a first power transmission unit 64, a second power transmission unit 65, a third power transmission unit 66, and a fourth power transmission unit 67.

  The first inner ring 61 engages with the first outer ring 62 via the first clutch portion 63. The power of the engine 2 is transmitted to the first inner ring 61. The first inner ring 61 is provided to rotate in response to the rotation of the output shaft of the engine 2. Specifically, the first inner ring 61 is provided to rotate integrally with the output shaft of the engine 2.

  The first outer ring 62 is connected to the rotation shaft of the M / G 4 via the first power transmission unit 64, and is connected to the rotation shaft of the pump 5 via the second power transmission unit 65. The first outer ring 62 is connected to the rotary shaft of the air compressor 14 for air conditioning of the vehicle via the third power transmission unit 66, and is connected to the rotary shaft of the water pump 15 via the fourth power transmission unit 67. The first power transmission unit 64, the second power transmission unit 65, the third power transmission unit 66, and the fourth power transmission unit 67 can be configured by, for example, a belt or a chain. The first power transmission unit 64, the second power transmission unit 65, the third power transmission unit 66, and the fourth power transmission unit 67 may be configured to further include, for example, a clutch that interrupts power.

  In the first clutch portion 63, the rotational speed of the first inner ring 61 obtained according to the driving of the engine 2 is transmitted from the primary pulley 81 (driving wheel 11) via the driving of the M / G 4 or the second one-way clutch 9. The first inner ring 61 is engaged with the first outer ring 62 when the rotational speed of the first outer ring 62 is higher than the rotational speed of the first outer ring 62 obtained according to the required power, and the power is transmitted from the first inner ring 61 to the first outer ring 62 . In addition, the first clutch portion 63 is a first outer ring obtained according to the drive of the M / G 4 and the power transmitted from the primary pulley 81, the rotational speed of the first inner ring 61 obtained according to the drive of the engine 2 When it is lower than the rotational speed of 62, the engagement between the first inner ring 61 and the first outer ring 62 is released, and power transmission from the first inner ring 61 to the first outer ring 62 is cut off.

  The rotational speed of the first inner ring 61 obtained according to the drive of the engine 2 constitutes a rotational speed Ne that is the engine-side rotational speed of the first one-way clutch 6. Further, the rotational speed of the first outer ring 62 obtained according to the drive of the M / G 4 and the power transmitted from the primary pulley 81 constitutes the rotational speed Nm1 which is the motor-side rotational speed of the first one-way clutch 6.

  Therefore, in the first one-way clutch 6, when the rotational speed Ne is higher than the rotational speed Nm1, the first inner ring 61 rotates the first outer ring 62 via the first clutch portion 63, and the power of the engine 2 is pumped Transmit to 5. On the other hand, when the rotational speed Ne is lower than the rotational speed Nm1, such as when the engine 2 is stopped during traveling, the first outer ring 62 does not rotate the first inner ring 61, and the first inner ring 61 and the first outer ring 62 rotate freely with one another. Therefore, power transmission between the engine 2 and the pump 5 and the M / G 4 is shut off.

  In the vehicle 1 of the present embodiment, power transmission and power transmission from the engine 2 to the pump 5 are performed by the first power transmission device 110 configured to include the first one-way clutch 6 and the second power transmission portion 65 as described above. Can be cut off.

  The forward / reverse switching mechanism 7 is provided between the engine 2 and the variator 8, specifically, between the first one-way clutch 6 and the variator 8. The forward / reverse switching mechanism 7 switches the rotation direction of the input rotation between the forward rotation direction corresponding to forward traveling and the reverse rotation direction corresponding to backward traveling.

  Specifically, the forward / reverse switching mechanism 7 includes a forward clutch 71 and a reverse brake 72. The forward clutch 71 is connected when the rotational direction is the normal direction. The reverse brake 72 is connected when the direction of rotation is the reverse direction. One of the forward clutch 71 and the reverse brake 72 can be configured as a clutch that interrupts the rotation between the engine 2 and the variator 8. When the forward clutch 71 of the forward / reverse switching mechanism 7 and the reverse brake 72 are released, power transmission between the engine 2 and the variator 8 is interrupted.

  The variator 8 has a primary pulley 81, a secondary pulley 82, and a belt 83 wound around the primary pulley 81 and the secondary pulley 82. Hereinafter, the primary is also referred to as PRI, and the secondary is also referred to as SEC. The variator 8 constitutes a belt-type continuously variable transmission mechanism that performs gear change by changing the groove diameter of the PRI pulley 81 and the SEC pulley 82 to change the winding diameter of the belt 83.

  The PRI pulley 81 has a fixed pulley 81a, a movable pulley 81b, and a PRI chamber 81c. In PRI pulley 81, by controlling the primary pressure supplied to PRI chamber 81c, movable pulley 81b is operated, and the groove width of PRI pulley 81 is changed.

  The SEC pulley 82 has a fixed pulley 82a, a movable pulley 82b, and an SEC chamber 82c. In the SEC pulley 82, the movable pulley 82b is operated by controlling the secondary pressure supplied to the SEC chamber 82c, and the groove width of the SEC pulley 82 is changed.

  The belt 83 has a V-shaped sheave surface formed by the fixed pulley 81a and the movable pulley 81b of the PRI pulley 81, and a V-shaped formed by the fixed pulley 82a and the movable pulley 82b of the SEC pulley 82. It is wound around the sheave surface.

  The second one-way clutch 9 is provided at the rear of the PRI pulley 81. The second one-way clutch 9 includes a second inner ring 91, a second outer ring 92, and a second clutch portion 93. In addition, a fifth power transmission unit 94 is provided in the second one-way clutch 9.

  The second inner ring 91 engages with the second outer ring 92 via the second clutch portion 93. The second inner ring 91 is connected to the rotation shaft of the fixed pulley 81 a of the PRI pulley 81, and the rotation of the fixed pulley 81 a is transmitted to the second inner ring 91.

  The second outer ring 92 is connected to the rotational shaft of the M / G 4 via the fifth power transmission unit 94. The fifth power transmission unit 94 can be configured by, for example, a belt or a chain. The fifth power transmission unit 94 may further include, for example, a clutch that interrupts power.

  When the rotational speed of the second inner ring 91 obtained according to the rotation of the PRI pulley 81 is higher than the rotational speed of the second outer ring 92, the second clutch portion 93 is used as the second inner ring 91 and the second outer ring 92. Engaging and transmitting power from the second inner ring 91 to the second outer ring 92. Also, when the rotational speed of the second inner ring 91 is lower than the rotational speed of the second outer ring 92, the second clutch unit 93 releases the engagement between the second inner ring 91 and the second outer ring 92, Power transmission from the inner ring 91 to the second outer ring 92 is shut off.

  The rotational speed of the second inner ring 91 to which the rotation of the PRI pulley 81 is transmitted constitutes a rotational speed Npri that is the rotational speed at the PRI pulley 81 side of the second one-way clutch 9. Further, the rotational speed of the second outer ring 92 constitutes a rotational speed Nm2 that is the motor-side rotational speed of the second one-way clutch 9.

  Therefore, in the second one-way clutch 9, when the rotational speed Npri is higher than the rotational speed Nm2, the second inner ring 91 rotates the second outer ring 92 via the second clutch portion 93 to rotate the PRI pulley 81. Transmit to the pump 5. On the other hand, when the rotational speed Npri is lower than the rotational speed Nm2, the second outer ring 92 does not rotate the second inner ring 91, and the second inner ring 91 and the second outer ring 92 rotate freely. Therefore, the rotation of the PRI pulley 81 is not transmitted to the pump 5.

  As described above, in the vehicle 1 of the present embodiment, the rotation of the PRI pulley 81 can be transmitted to the rotation shaft of the M / G 4 via the second one-way clutch 9. In addition, the second one-way clutch 9, the fifth power transmission unit 94, the rotating shaft of the M / G 4, the first power transmission unit 64, the first outer ring 62 (first one-way clutch 6), and the second power transmission unit 65 are included. By means of the second power transmission device 120 configured as described above, power transmission and transmission of power from the drive wheel 11 to the pump 5 can be interrupted. The second power transmission device 120 shuts off power transmission and power transmission from the drive wheel 11 to the pump 5 via the variator 8.

  Therefore, the power transmission between the engine 2 and the variator 8 is interrupted by the forward / reverse switching mechanism 7 and the rotation of the PRI pulley 81 is pumped through the second power transmission device 120 even when the engine 2 is stopped. 5, and the pump 5 can be driven. That is, power can be transmitted from the drive wheel 11 to the pump 5 by the fifth power transmission unit 94.

  When the engine 2 is not stopped and power transmission between the engine 2 and the variator 8 is performed by the forward / reverse switching mechanism 7, the rotational speed Npri of the second inner ring 91 is the rotation of the second outer ring 92. The second one-way clutch 9 and the fifth power transmission unit 94 are configured to be lower than the speed Nm2.

  In addition, the second outer ring 92 may be directly connected to the rotation shaft of the pump 5 via the fifth power transmission unit 94.

  The second power transmission device 120 constitutes a power transmission device 150 which is a power transmission device to the pump 5 together with the first power transmission device 110. The power transmission device 150 transmits power by another power transmission device when performing power transmission by any of the first power transmission device 110, the second power transmission device 120, and the third power transmission device described below. Shut off the

  In the present embodiment, the second power transmission device 120 is further configured as a third power transmission device that performs power transmission from the M / G 4 to the pump 5 and shuts off the power transmission. In other words, the second power transmission device 120 is configured to double as the third power transmission device. The second power transmission device 120 functions as a third power transmission device, for example, as follows.

  That is, when the power transmission from drive wheel 11 to pump 5 is being performed by second power transmission device 120, M / G 4 is driven to set the rotational speed Nm2 of second outer ring 92 to the rotational speed of second inner ring 91 The engagement of the second one-way clutch 9 can be released by raising the pressure than Npri.

  In such a case, the second power transmission device 120 performs the power transmission from the M / G 4 to the pump 5 at the same time as blocking the power transmission from the drive wheel 11 to the pump 5, thereby the third power It also functions as a transmission device.

  In addition, when the power transmission from the M / G 4 to the pump 5 is being performed, the drive of the M / G 4 is stopped, and the rotation speed Nm 2 of the second outer ring 92 is made lower than the rotation speed Npri of the second inner ring 91 Thus, the second one-way clutch 9 can be engaged.

  In such a case, the second power transmission device 120 performs power transmission from the drive wheel 11 to the pump 5 and simultaneously shuts off the power transmission from the M / G 4 to the pump 5 to generate the third power. It also functions as a transmission device.

  The second one-way clutch 9 is provided in a third power transmission device, which serves as the second power transmission device 120 and the second power transmission device 120, and is a drive wheel having the second inner ring 91 as one fastening element via the variator 8 The power from M. 11 is input, and a clutch is also configured in which the power of M / G 4 is input to the second outer ring 92 which is the other fastening element.

  The final reduction gear mechanism 10 transmits the output rotation from the variator 8 to the drive wheel 11. The final reduction gear mechanism 10 is configured to have a plurality of gear trains and differential gears. The final reduction gear mechanism 10 rotates the drive wheel 11 via an axle.

  The hydraulic circuit 100 includes a plurality of flow paths and a plurality of hydraulic control valves. The hydraulic circuit 100 adjusts the necessary hydraulic pressure from the hydraulic pressure generated by the oil discharged from the pump 5 based on the signal from the controller 12. Then, the hydraulic circuit 100 supplies the adjusted hydraulic pressure as the primary pressure to the PRI pulley 81 of the variator 8 and supplies the adjusted hydraulic pressure as the secondary pressure to the SEC pulley 82. The hydraulic circuit 100 also supplies hydraulic pressure to the forward / reverse switching mechanism 7 and the torque converter 3.

  The vehicle 1 further comprises a controller 12. The controller 12 is an electronic control unit, and a signal from the sensor switch group 13 is input to the controller 12.

  The sensor switch group 13 includes, for example, an accelerator opening sensor that detects an accelerator opening APO, a brake sensor that detects a brake depression force based on a depression amount BRP of a brake pedal, a vehicle speed sensor that detects a vehicle speed VSP, and a rotational speed Ne Includes an engine rotational speed sensor that detects

  The sensor switch group 13 further includes, for example, a PRI pressure sensor that detects a PRI pressure, an SEC pressure sensor that detects an SEC pressure, a PRI rotation speed sensor that detects a rotation speed Npri that is the input side rotation speed of the PRI pulley 81, And an SEC rotation speed sensor that detects a rotation speed Nsec that is an output side rotation speed of the SEC pulley 82, and an inhibitor switch that detects an operation position of the shift lever.

  The controller 12 controls the M / G 4 and the hydraulic circuit 100 based on signals from the sensor switch group 13. The transmission ratio of the variator 8 is changed by the controller 12 and the hydraulic circuit 100 by controlling the oil discharged by the pump 5.

  By the way, in the vehicle 1, in order to improve the fuel consumption of the engine 2, the sailing stop control is performed. The sailing stop control is an inertia running control that performs inertia running by automatically stopping the engine 2 when the vehicle 1 is running, for example, when the vehicle speed VSP is higher than a predetermined vehicle speed and the accelerator pedal is not depressed, and the brake pedal It is executed when there is no stepping on the Further, the sailing stop control can be performed when the gear ratio of the variator 8 is the minimum gear ratio. In the present embodiment, these four conditions constitute the execution condition of the sailing stop control. Below, sailing stop control is only called SS control.

  During the SS control, the engine 2 is stopped, the forward clutch 71 of the forward / reverse switching mechanism 7 and the reverse brake 72 are released, and power transmission between the engine 2 and the variator 8 is cut off. Therefore, in the power transmission device 150, power transmission from the engine 2 to the pump 5 via the first one-way clutch 6 by the first power transmission device 110 is not performed.

  During SS control, the power transmission device 150 transmits power from the drive wheel 11 to the pump 5 through the PRI pulley 81 of the variator 8, the second one-way clutch 9 and the like by the second power transmission device 120.

  When the pump 5 is driven by power transmission from the drive wheel 11, the discharge amount of the pump 5 is determined according to the rotational speed Npri (vehicle speed VSP) of the PRI pulley 81. In the power transmission path from the engine 2 to the drive wheel 11, the rotational speed Npri of the PRI pulley 81 provided on the engine 2 side constitutes the input side rotational speed of the variator 8.

  In the vehicle 1, a pump system 200 is configured to include a pump 5, a power transmission device 150, a controller 12 and a hydraulic circuit 100.

  Next, an example of control performed by the controller 12 will be described using the flowchart shown in FIG.

  In step S1, the controller 12 determines whether SS control is in progress. Such a determination can be made, for example, by determining whether the execution condition of the SS control is satisfied and the restart condition of the engine 2 is not satisfied.

  The restart condition of the engine 2 can be, for example, a condition including that the accelerator pedal has been depressed and therefore that an acceleration request to the engine 2 has been made. The restart condition of the engine 2 may be that the execution condition of the SS control has not been established.

  If a negative determination is made in step S1, the process proceeds to step S10. In step S10, the controller 12 permits execution of the drive of the pump 5 by the M / G 4. After the step S10, the present flowchart is temporarily ended.

  If it is affirmation determination by step S1, a process will progress to step S2. In step S2, the controller 12 executes transmission ratio control of the variator 8. The gear ratio control will be described later.

  In step S3, the controller 12 determines whether SOC (state of charge) is larger than a first predetermined amount α. The SOC is a state amount indicating the charge state of the battery 42, and is, for example, a storage amount of the battery 42. The first predetermined amount α is a value for determining whether or not the battery 42 has a margin, and is, for example, a storage amount to be secured at a minimum. The first predetermined amount α can be set in advance based on an experiment or the like.

  If the determination in step S3 is affirmative, the process proceeds to step S4. In step S4, the controller 12 determines whether execution of driving of the pump 5 by the M / G 4 is permitted. If it is affirmation determination by step S4, a process will progress to step S5.

  In step S5, the controller 12 drives the M / G 4 to drive the pump 5 by the M / G 4. Specifically, the controller 12 drives the M / G 4 to release the engagement of the second one-way clutch 9.

  As a result, power transmission from the M / G 4 to the pump 5 by the third power transmission device can be performed by the power transmission device 150, so the pump 5 can be driven by the M / G 4. After step S5, the process of this flowchart is once ended.

  Thereafter, when the SOC decreases and the negative determination is made in step S3, the process proceeds to step S6. In step S6, the controller 12 stops M / G4. As a result, the second one-way clutch 9 is engaged, and power transmission from the drive wheel 11 to the pump 5 by the second power transmission device 120 can be performed by the power transmission device 150. The pump 5 can be driven.

  Subsequently, in step S7, the controller 12 prohibits the execution of the drive of the pump 5 by the M / G 4. After step S7, the process of this flowchart is temporarily ended.

  After that, when an affirmative determination is made in step S3, as a result of the negative determination in step S4, the process proceeds to step S8. In step S8, the controller 12 determines whether the SOC exceeds the second predetermined amount β. The second predetermined amount β is set to a value larger than the first predetermined amount α. The second predetermined amount β is a value for setting a hysteresis, that is, a dead zone, and can be set in advance based on an experiment or the like.

  If the determination in step S8 is negative, the process proceeds to step S6. Therefore, in this case, even if the SOC is larger than the first predetermined amount α, driving of the pump 5 by the M / G 4 is not performed.

  If the determination in step S8 is affirmative, the process proceeds to step S9, and the controller 12 permits the execution of the drive of the pump 5 by the M / G 4. After step S9, the process proceeds to step 5.

  In this flowchart, the controller 12 prohibits the execution of the drive of the pump 5 by the M / G 4 until an affirmative determination is made in step S8 when a negative determination is made in step S3 during SS control. That is, when the SOC is smaller than the first predetermined amount α during the SS control, the controller 12 prohibits the execution of the drive of the pump 5 by the M / G 4 until the SOC exceeds the second predetermined amount β. Do.

  In step S2, the controller 12 controls the transmission ratio of the variator 8 such that the rotational speed Npri becomes lower than the first predetermined rotational speed Npri1.

  The first predetermined rotation speed Npri1 is the rotation speed Ne set to the engine 2 when there is no acceleration request to the engine 2, and hence the rotation speed Npri corresponding to the idle rotation speed, and is, for example, 1,100 rpm. The rotational speed Npri corresponding to the rotational speed Ne can be set to the rotational speed Ne when the rotational speed Ne is transmitted from the engine 2 to the variator 8 as it is, and the rotational speed Ne is changed from the engine 2 to the variator 8 In the case of transmission, it is possible to make the rotational speed different from the rotational speed Ne by the amount to be changed. In the present embodiment, the first predetermined rotation speed Npri1 is set to the rotation speed Npri corresponding to the lowest value of the idle rotation speed. The first predetermined rotation speed Npri1 may be a variable value according to the operating state of the vehicle 1, such as the coolant temperature of the engine 2, for example.

  Specifically, the controller 12 controls the transmission ratio of the variator 8 such that the rotation speed Npri becomes a second predetermined rotation speed Npri2 lower than the first predetermined rotation speed Npri1.

  The second predetermined rotation speed Npri2 is a rotation speed Npri corresponding to the required discharge amount required by the pump 5 during SS control, and is, for example, 500 rpm. The required discharge amount can be preset based on experiments or the like according to the state of the vehicle 1 in which the SS control is performed. The second predetermined rotation speed Npri1 may be a variable value corresponding to the operating state of the vehicle 1, such as the temperature of the oil discharged by the pump 5, for example.

  More specifically, the controller 12 switches the shift lines as described below, and controls the transmission ratio of the variator 8 according to the switched shift lines.

  FIG. 3 is a view showing an example of a shift map. The variator 8 is shifted based on the shift map. In the shift map, the operating point of the variator 8 is shown according to the vehicle speed VSP and the rotational speed Npri.

  In the shift map, the transmission ratio of the variator 8 is indicated by the slope of a line connecting the operating point of the variator 8 and the zero point of the shift map. The shift of the variator 8 can be performed between the lowest line obtained by maximizing the transmission ratio of the variator 8 and the highest line obtained by minimizing the transmission ratio of the variator 8.

  The shift of the variator 8 is performed according to a shift line selected according to the accelerator opening APO. For this reason, in the shift map, shift lines are set for each accelerator opening APO. In FIG. 3, the first shift line L <b> 1 and the second shift line L <b> 2, which are shift lines when the accelerator opening APO = 0, are illustrated as the shift lines. The shift line indicates the transmission ratio setting of the variator 8 according to the vehicle speed VSP.

  The first shift line L1 is set to the Highest line when the vehicle speed VSP is higher than the first High-side vehicle speed VSP11, and makes the gear ratio of the variator 8 the minimum gear ratio. The first shift line L1 causes the rotational speed Npri to become the first predetermined rotational speed Npri1 when the transmission ratio of the variator 8 is made larger than the minimum transmission ratio, and therefore when the vehicle speed VSP falls below the first high side vehicle speed VSP11. It is set.

  Specifically, the first speed change line L1 controls the speed ratio of the variator 8 within a speed ratio range larger than the minimum speed ratio and smaller than the maximum speed ratio. Specifically, the vehicle speed VSP is lower than the first high side vehicle speed VSP11. When the vehicle speed is higher than the first low vehicle speed VSP12, the rotational speed Npri is set to be the first predetermined rotational speed Npri1. The first shift line L1 is set to the lowest level when the gear ratio of the variator 8 is set to the maximum gear ratio, specifically, when the vehicle speed VSP is lower than the first low vehicle speed VSP12.

  The first shift line is specifically a coast line. Therefore, during coasting, the first predetermined rotation speed Npri is the rotation speed Npri set according to the shift of the variator 8, that is, the transmission ratio of the variator 8 is larger than the minimum transmission ratio and smaller than the maximum transmission ratio. The rotational speed Npri set when controlling within the range is configured.

  During coasting, a driving state in which power from the drive wheels 11 is transmitted to the engine 2 can be obtained. Further, during coasting, the engine 2 can be in a traveling state in which the engine 2 is automatically stopped. In this case, the first predetermined rotation speed Npri can be set to the rotation speed Npri corresponding to the cranking rotation speed, which is the rotation speed Ne at the time of starting the engine 2.

  The second shift line L2 is set to the Highest line when the vehicle speed VSP is higher than the second High-side vehicle speed VSP21, and sets the gear ratio of the variator 8 to the minimum gear ratio. The second high vehicle speed VSP21 is set to be lower than the first high vehicle speed VSP11. For this reason, when making the gear ratio of the variator 8 larger than the minimum gear ratio, the second shift line L2 is set such that the rotational speed Npri is lower than the first predetermined rotational speed Npri1. The second shift line L2 is set such that the rotational speed Npri becomes equal to the second predetermined rotational speed Npri2 when the transmission ratio of the variator 8 is made larger than the minimum transmission ratio.

  Specifically, when the second shift line L2 controls the gear ratio of the variator 8 within a gear ratio range larger than the minimum gear ratio and smaller than the maximum gear ratio, specifically, the vehicle speed VSP is lower than the second High side vehicle speed VSP21. When the vehicle speed is higher than the second low vehicle speed VSP22, the rotational speed Npri is set to be the second predetermined rotational speed Npri2. The second shift line L2 is set to the lowest level when the gear ratio of the variator 8 is set to the maximum gear ratio, specifically, when the vehicle speed VSP is lower than the second low vehicle speed VSP22.

  In step S2 of the flowchart shown in FIG. 2 described above, the controller 12 switches the shift line to the second shift line L2 and performs the gear ratio control in accordance with the switched second shift line L2. The controller 12 switches the shift line from the first shift line L1 to the second shift line L2.

  FIG. 4 is a diagram showing an example of a timing chart corresponding to the control performed by the controller 12. At timing T1, the accelerator opening APO becomes zero. As a result, from the timing T1, the rotational speed Ne starts to decrease.

  At this time, power transmission between the engine 2 and the variator 8 is not cut off. Therefore, the work of the rotational speed Npri and the work of the pump 5 also start to decrease according to the decrease of the rotational speed Ne. In addition, deceleration occurs and the vehicle speed VSP also starts to decrease. At timing T1, the shift line is switched to the first shift line L1. Therefore, from timing T1, the transmission ratio of the variator 8 starts to decrease toward the minimum transmission ratio. From timing T1 to timing T2, M / G 4 is stopped and SOC is not reduced.

  At timing T2, the transmission ratio of the variator 8 becomes the minimum transmission ratio. As a result, SS control is started. In the SS control, the engine 2 is stopped. For this reason, from the timing T2, the rotational speed Ne starts to decrease greatly. In SS control, power transmission between the engine 2 and the variator 8 is cut off. Therefore, from the timing T2, the deceleration is significantly reduced, and the decrease in the vehicle speed VSP is suppressed. At timing T2, the shift line is switched from the first shift line L1 to the second shift line L2.

  At timing T2, the SOC is larger than the first predetermined amount α. Therefore, at timing T2, the drive of M / G 4 is started, and the output of M / G 4 becomes large. M / G 4 is controlled such that the rotational speed Nm 2 of the second outer ring 92 is slightly higher than the rotational speed Npri of the second inner ring 91. For this reason, from timing T2, the engagement of the second one-way clutch 9 is released, and the pump 5 is driven by the M / G 4. Moreover, according to the output of M / G4, while work of pump 5 occurs, SOC falls.

  From timing T2, rotational speed Npri gradually decreases in accordance with vehicle speed VSP. The output of the M / G 4 is reduced according to the rotational speed Npri so that the second one-way clutch 9 is not engaged. At this time, the M / G 4 is controlled such that the work of the pump 5 becomes the required work required by the pump 5 during SS control.

  At timing T3, the rotational speed Npri becomes the first predetermined rotational speed Npri1. However, since the shift line is switched to the second shift line L2, the rotational speed Npri continues to decrease according to the vehicle speed VSP even after the timing T3. The output of M / G 4 is also continuously reduced according to the rotational speed Npri.

  At timing T4, the rotational speed Npri becomes the second predetermined rotational speed Npri2. Also, the work of the pump 5 is a necessary work during SS control. As a result, the required discharge amount required by the pump 5 during SS control is secured.

  From timing T4, the transmission gear ratio of the variator 8 is controlled so that the rotational speed Npri becomes equal to the second predetermined rotational speed Npri2. As a result, the outputs of the rotational speeds Npri and M / G4 and the work of the pump 5 are maintained as they are.

  The SOC falls below the second predetermined amount β between timing T3 and timing T4 and falls below the first predetermined amount α at timing T5. Therefore, at timing T5, the M / G 4 stops and the output of the M / G 4 becomes zero. Thus, the second one-way clutch 9 is engaged, and the pump 5 is driven by the power from the drive wheel 11. From timing T5, during SS control, execution of driving of the pump 5 by the M / G 4 is also prohibited until the SOC exceeds the second predetermined amount β.

  In addition, the work of the pump 5 obtained according to the power of M / G 4 at timing T4 is actually larger than the required work during SS control. However, since the difference is small because the M / G 4 is controlled so that the rotational speed Nm2 of the second outer ring 92 becomes slightly higher than the rotational speed Npri of the second inner ring 91, the pump obtained here at timing T4 We described the work of 5 as the required work in SS control.

  Related to this, it is also possible to make the work of the pump 5 obtained according to the power of the M / G 4 more strictly necessary work during SS control. For this purpose, the second predetermined rotational speed Npri2 used in the transmission ratio control of the Bayer 8 is set to a lower value, and the rotational speed Nm2 of the second outer ring 92 is reduced to the original second predetermined rotational speed Npri2. Good.

  At this time, in the transmission ratio control of the Bayer 8, the rotational speed difference set between the rotational speed Nm 2 of the second outer ring 92 and the rotational speed Npri of the second inner ring 91 in order to put the second one-way clutch 9 in the engagement release state. The second predetermined rotation speed Npri2 may be set to be lower by an amount.

  Next, main operational effects of the pump system 200 will be described. The pump system 200 includes a pump 5, a M / G 4, a first power transmission device 110, a second power transmission device 120, and a third power transmission device serving as the second power transmission device 120. The power transmission unit 150 performs power transmission from the drive wheel 11 to the pump 5 by the power transmission unit 120, and drives the M / G 4 when the SOC is larger than the first predetermined amount α during SS control, and the third power And a controller 12 as a control unit that causes the transmission device to transmit power from the M / G 4 to the pump 5.

  According to the pump system 200 having such a configuration, when the battery 42 has a margin, kinetic energy of the vehicle 1 is not consumed by the pump 5 by driving the pump 5 with the M / G 4 during SS control. Can be Therefore, when driving the pump 5 with power from the drive wheel 11 during SS control, fuel efficiency can be improved by improving the inertia travel distance (effects corresponding to claims 1 and 4).

  The pump system 200 further includes a controller 12 as a transmission ratio control unit that controls the transmission ratio of the variator 8. The second power transmission device 120 is provided to cut off power transmission and transmission of power from the drive wheel 11 to the pump 5 via the variator 8. Power transmission device 150 further includes a second one-way clutch 9. When driving the M / G 4, the controller 12 as a control unit controls the M / G 4 so that the rotational speed Nm 2 of the second outer ring 92 becomes higher than the rotational speed Npri of the second inner ring 91. The controller 12 as the transmission ratio control unit controls the transmission ratio of the variator 8 such that the rotational speed Npri becomes lower than the first predetermined rotational speed Npri1 during SS control.

  According to the pump system 200 having such a configuration, when the pump 5 is driven by the M / G 4 during SS control, the work of the pump 5 becomes the required work during SS control, that is, M / G 4 as much as possible Can reduce the output of For this reason, the power consumption of the battery 42 can be suppressed to the extent that the M / G 4 does not generate an output that is larger than necessary. As a result, since it is possible to continue to drive the pump 5 for a long time by the M / G 4 as the SOC is less likely to fall below the first predetermined amount α during SS control, further fuel efficiency improvement can be achieved by the improvement of the coasting distance. (Effect corresponding to claim 2).

  In the pump system 200, when the SOC is smaller than the first predetermined amount α during SS control, the controller 12 as the controller controls the pump by the M / G 4 until the SOC exceeds the second predetermined amount β. Prohibit the execution of drive 5.

  According to the pump system 200 having such a configuration, by providing the hysteresis, the drive and stop of the M / G 4 are prevented from being repeated unnecessarily even if the SOC fluctuates around the first predetermined amount α. Yes (effect corresponding to claim 3).

  As mentioned above, although embodiment of this invention was described, the said embodiment only shows a part of application example of this invention, The scope which limits the technical scope of this invention to the specific structure of the said embodiment is not.

  In the above embodiment, the second inner ring 91 is connected to the rotary shaft of the fixed pulley 81a of the PRI pulley 81. For example, the second inner ring 91 is connected to the rotary member between the forward / reverse switching mechanism 7 and the variator 8 It is also possible to transmit power from 11 to the pump 5.

  In the above embodiment, the case where the power transmission device 150 is configured to have the first one-way clutch 6 and the second one-way clutch 9 has been described. However, instead of the first one-way clutch 6 or the second one-way clutch 9, for example, a friction clutch may be used in the power transmission device 150. In this case, the power transmission device 150 further includes, for example, a controller 12 and a hydraulic circuit 100 configured to cause the friction clutch to perform power transmission similar to that of the first one-way clutch 6 and the second one-way clutch 9. It can be grasped.

  In the above-mentioned embodiment, the case where the 2nd power transmission device 120 serves as the 3rd power transmission device was explained. However, the third power transmission device may be provided as a power transmission device different from the second power transmission device 120.

  In the above embodiment, the case where the traveling drive source is the engine 2 has been described. However, the traveling drive source may be, for example, a motor, the engine 2 and the motor.

  The above embodiment has described the case where the variator 8 is a belt-type continuously variable transmission mechanism. However, the variator 8 may be, for example, a toroidal type continuously variable transmission mechanism.

  In the above embodiment, the case where the transmission gear ratio of the variator 8 is controlled according to the shift line such as the second shift line L2 specified on the shift map has been described. However, controlling the transmission ratio of the variator 8 according to the transmission line includes, for example, controlling the transmission ratio of the variator 8 according to the transmission line defined by the arithmetic expression.

1 Vehicle 2 Engine (Drive Source)
5 Pump 7 Forward / backward switching mechanism 8 Variator 11 Drive wheel 12 Controller (gear ratio control section)
100 hydraulic circuit 110 first power transmission device 120 second power transmission device 150 power transmission device 200 pump system

Claims (3)

An oil pump driven by a vehicle drive power source to discharge oil;
A motor provided to drive the oil pump;
Provided as a power transmission device to the oil pump,
A first power transmission device for interrupting power transmission and power transmission from the traveling drive source to the oil pump;
A second power transmission device for interrupting power transmission and power transmission from a drive wheel of the vehicle to the oil pump;
And a third power transmission device for blocking power transmission and power transmission from the motor to the oil pump,
A power transmission device for performing power transmission from the drive wheel to the oil pump by the second power transmission device during inertial traveling control in which inertial traveling is performed by automatically stopping the traveling drive source when the vehicle is traveling; ,
The motor is driven when the state quantity indicating the state of charge of the battery for supplying the electric power to the motor is larger than the first predetermined amount during the inertial running control, and the third power transmission device transmits the electric power from the motor A control unit for transmitting power to the oil pump;
A transmission ratio control unit configured to control a transmission ratio of a variator provided in a power transmission path for transmitting power from the traveling drive source to the drive wheels;
Equipped with
The second power transmission device is provided to interrupt power transmission and power transmission from the drive wheel to the oil pump via the variator.
The power transmission device is provided in the second power transmission device and the third power transmission device, and power from the drive wheel via the variator is input to one of the fastening elements, and the other of the other fastening elements is provided. Further including a clutch into which the power of the motor is input;
The clutch is
When the rotational speed of the one fastening element is higher than the rotational speed of the other fastening element, power transmission from the drive wheel to the oil pump is performed by the second power transmission device,
If the rotational speed of the other fastening element is higher than the rotational speed of the one fastening element, power transmission from the motor to the oil pump is performed by the third power transmission device.
In driving the motor, the control unit controls the motor such that the rotational speed of the other fastening element is higher than the rotational speed of the one fastening element,
The transmission ratio control unit controls the transmission ratio of the variator such that the input side rotational speed of the variator becomes a second predetermined rotational speed lower than a first predetermined rotational speed during the inertial traveling control.
The first predetermined rotation speed and the second predetermined rotation speed control the gear ratio of the variator within the gear ratio range larger than the minimum gear ratio and smaller than the maximum gear ratio according to the vehicle speed during the inertial traveling control The input-side rotational speed of the variator, which is set when
Pump system characterized by   The pump system according to claim 1, wherein
  When the state quantity is smaller than the first predetermined amount during the inertial running control, the control unit is configured to exceed the second predetermined amount in which the state amount is larger than the first predetermined amount. Prohibit the driving of the oil pump by the motor
Pump system characterized by An oil pump driven by a traveling drive source of a vehicle to discharge oil, a motor provided to drive the oil pump, and a power transmission device to the oil pump are provided from the traveling drive source A first power transmission device that performs power transmission to the oil pump and blocking the power transmission; a second power transmission device that blocks power transmission from the drive wheel of the vehicle to the oil pump; and the motor A third power transmission device for transmitting power from the engine to the oil pump and interrupting the power transmission, and during freewheeling control for performing freewheeling by automatically stopping the driving source for traveling when the vehicle is traveling , be transmitted and a power transmission device which transmits power to the oil pump from the drive wheel, power to the drive wheel from the traveling drive source by the second power transmission device And a variator provided on the power transmission path, the second power transmission device is provided from the drive wheel through the variator to perform blocking of the power transmission and power transmission to the oil pump, the power The transmission device is provided in the second power transmission device and the third power transmission device, and power from the drive wheel via the variator is input to one of the fastening elements, and the motor is provided in the other fastening element. The clutch further includes a clutch to which power of the clutch is input, the clutch being driven by the second power transmission device from the drive wheel when the rotational speed of the one fastening element is higher than the rotational speed of the other fastening element When the power transmission to the oil pump is performed, and the rotational speed of the other fastening element is higher than the rotational speed of the one fastening element, the third operation is performed. A control method for controlling a pumping system to perform power transmission to the oil pump from the motor by the force transmission device,
The rotational speed of the other fastening element is the rotational speed of the one fastening element when the state quantity indicating the charge state of the battery for supplying power to the motor is larger than the first predetermined quantity during the inertial running control. Driving the motor so as to be higher than the above and causing the power transmission device to perform power transmission from the motor to the oil pump by the third power transmission device ;
Controlling the gear ratio of the variator such that the input side rotational speed of the variator becomes a second predetermined rotational speed lower than a first predetermined rotational speed during the inertia running control;
Only including,
The first predetermined rotation speed and the second predetermined rotation speed are controlled within the transmission ratio range in which the transmission ratio of the variator is larger than the minimum transmission ratio and smaller than the maximum transmission ratio according to the vehicle speed during the inertial traveling control. And the input-side rotational speed of the variator, which is set when
Method of controlling a pump system characterized in that.

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