JP2019120306A - Power transmission device and control method of power transmission device - Google Patents

Abstract

To provide a power transmission device capable of supplying oil necessary in select control even when a mechanical oil pump is miniaturized along with performing gear change of a continuously variable transmission mechanism by an electric oil pump.SOLUTION: A power transmission device includes a variator 2 and a clutch 40, and an electric oil pump 32. The power transmission device is constituted so as to control the supply/discharge of oil in a PRI pulley oil chamber 21c by the electric oil pump 32, and includes a controller 10 for performing select control when a driver performs a select operation. The controller 10 is constituted so as to supply oil to a clutch oil chamber 40a by the electric oil pump 32 during select control.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a power transmission device and a control method of the power transmission device.

  Patent Document 1 discloses a transmission drive apparatus including a continuously variable transmission and a clutch, a mechanical oil pump, and an electric oil pump.

  The mechanical oil pump is driven by the engine and configured to be able to supply the oil of the oil reservoir to the secondary pulley oil chamber and the clutch of the continuously variable transmission. The electric oil pump is provided in an oil passage connecting the primary pulley oil chamber and the secondary pulley oil chamber of the continuously variable transmission, and is configured to be able to supply the oil of the oil reservoir to the clutch. The shifting of the continuously variable transmission is performed by causing the electric oil pump to move oil into and out of the primary pulley oil chamber.

JP 2005-30495 A

  When shifting the continuously variable transmission as described above, the shift required flow rate is covered by the electric oil pump. For this reason, in this case, the mechanical oil pump can be miniaturized as compared with the case where the flow required for shifting is secured by the mechanical oil pump.

  However, in the scene selected by the driver, the rotational speed of the engine is low and the rotational speed of the mechanical oil pump is also low. For this reason, when the mechanical oil pump is miniaturized, there is a possibility that the supply flow rate of the mechanical oil pump may be insufficient relative to the flow rate of oil necessary for the select control.

  The present invention has been made in view of such problems. Even if the mechanical oil pump is miniaturized in combination with shifting of the continuously variable transmission mechanism by the electric oil pump, the necessary oil is supplied by select control. It is an object of the present invention to provide a possible power transmission device and a control method of the power transmission device.

  In a power transmission apparatus according to an aspect of the present invention, a continuously variable transmission mechanism and a clutch for transmitting power between a drive source and a driving wheel communicate with a primary pulley oil chamber and a secondary pulley oil chamber of the continuously variable transmission mechanism. An electric oil pump provided in the first oil passage to be supplied and capable of supplying the oil in the oil reservoir to a clutch oil chamber which is the oil chamber of the clutch, the power transmission device comprising: The oil pump control unit controls oil in and out of the primary pulley oil chamber, and the clutch control unit performs select control to switch the clutch between the engaged state and the released state when the driver performs a select operation. . The oil pump control unit supplies oil to the clutch oil chamber by the electric oil pump during the select control.

  According to another aspect of the present invention, the continuously variable transmission mechanism and the clutch for transmitting power between the drive source and the drive wheels are communicated with the primary pulley oil chamber and the secondary pulley oil chamber of the continuously variable transmission mechanism. A control method of a power transmission device, comprising: an electric oil pump provided in a first oil passage and configured to be capable of supplying oil in an oil reservoir to a clutch oil chamber which is an oil chamber of the clutch Controlling the oil in / out of the primary pulley oil chamber with a pump, and performing select control to switch the clutch between a engaged state and a released state when a select operation is performed by a driver; The oil pump controls oil in and out of the primary pulley oil chamber, and the electric oil pump supplies oil to the clutch oil chamber during the select control. The method of the power transmission device is provided.

  According to these aspects, in addition to the mechanical oil pump, the required oil can be supplied by select control with the electric oil pump. For this reason, even if the mechanical oil pump is downsized in combination with the speed change of the continuously variable transmission mechanism by the electric oil pump, the necessary oil can be supplied by the select control.

It is a schematic block diagram which shows the principal part of a vehicle. It is FIG. 1 of the figure explaining the switching position of a switching valve. It is FIG. 2 of the figure explaining the switching position of a switching valve. It is a figure explaining the relationship between a supply flow rate and a required flow rate. It is a figure which shows an example of the control performed in 1st Embodiment with a flowchart. It is a figure which shows an example of the timing chart concerning 1st Embodiment. It is a figure which shows an example of the control performed in 2nd Embodiment by a flowchart. It is a figure which shows an example of the timing chart concerning 2nd Embodiment. It is a figure which shows an example of the control performed in 3rd Embodiment by a flowchart. It is a figure which shows an example of the timing chart concerning 3rd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the attached drawings.

First Embodiment
FIG. 1 is a schematic configuration view showing a main part of a vehicle. The transmission 1 is a belt-type continuously variable transmission and is mounted on a vehicle together with an engine ENG that constitutes a drive source of the vehicle. The rotation from the engine ENG is input to the transmission 1. The output rotation of the engine ENG is input to the transmission 1 via a torque converter TC or the like having a lockup clutch LU. The transmission 1 outputs the input rotation at a rotation according to the transmission gear ratio. The gear ratio is a value obtained by dividing the input rotation by the output rotation.

  The transmission 1 has a variator 2 and a hydraulic circuit 3.

  The variator 2 is provided in a power transmission path connecting the engine ENG and a drive wheel (not shown), and performs power transmission between them. The variator 2 is a belt type continuously variable transmission mechanism having a primary pulley 21, a secondary pulley 22, and a belt 23 wound around the primary pulley 21 and the secondary pulley 22.

  The variator 2 changes the winding diameter of the belt 23 by changing the groove widths of the primary pulley 21 and the secondary pulley 22 respectively, and performs a speed change. Hereinafter, the primary will be referred to as PRI and the secondary will be referred to as SEC.

  The PRI pulley 21 has a fixed pulley 21a, a movable pulley 21b, and a PRI pulley oil chamber 21c. In the PRI pulley 21, oil is supplied to the PRI pulley oil chamber 21c. When the movable pulley 21b is moved by the oil of the PRI pulley oil chamber 21c, the groove width of the PRI pulley 21 is changed.

  The SEC pulley 22 has a fixed pulley 22a, a movable pulley 22b, and an SEC pulley oil chamber 22c. In the SEC pulley 22, oil is supplied to the SEC pulley oil chamber 22c. When the movable pulley 22b is moved by the oil of the SEC pulley oil chamber 22c, the groove width of the SEC pulley 22 is changed.

  The belt 23 has a V-shaped sheave surface formed by the fixed pulley 21a and the movable pulley 21b of the PRI pulley 21 and a V-shaped formed by the fixed pulley 22a and the movable pulley 22b of the SEC pulley 22. It is wound around the sheave surface. The belt 23 is held by a belt clamping force generated by the SEC pressure Psec.

  The hydraulic circuit 3 switches the mechanical oil pump 31, the electric oil pump 32, the check valve 33, the line pressure adjusting valve 34, the line pressure solenoid 35, and the PRI pulley oil chamber 21c and the SEC pulley oil chamber 22c. A valve 36, an oil reservoir 37, a pilot valve 38, a clutch pressure solenoid 39, a clutch 40, and a T / C hydraulic system 41. These configurations constitute the hydraulic circuit 3 together with the oil passage as follows.

  The PRI pulley oil chamber 21c and the SEC pulley oil chamber 22c communicate with each other by the first oil passage R1. The mechanical oil pump 31 is connected to the first oil passage R1 via the discharge side oil passage Rout of the mechanical oil pump 31. The mechanical oil pump 31 is a mechanical oil pump driven by the power of the engine ENG, and is coupled to the impeller of the torque converter TC via a power transmission member, as schematically shown in a coupled state by a two-dot broken line.

  A check valve 33 is provided in the discharge side oil passage Rout. The check valve 33 blocks the flow of oil in the direction of the mechanical oil pump 31 and allows the flow of oil in the opposite direction. A line pressure adjusting valve 34 is connected to a portion of the discharge side oil passage Rout on the downstream side of the check valve 33.

  The line pressure adjusting valve 34 regulates the oil supplied from the mechanical oil pump 31 to the line pressure PL. The line pressure adjusting valve 34 operates in accordance with the solenoid pressure generated by the line pressure solenoid 35. In the present embodiment, the line pressure PL is supplied as the SEC pressure Psec to the SEC pulley oil chamber 22c.

  An electric oil pump 32 and a switching valve 36 are provided in the first oil passage R1. The electric oil pump 32 is provided at a portion closer to the PRI pulley oil chamber 21c than the first point C1 which is a point to which the discharge side oil passage Rout is connected in the first oil passage R1. The electric oil pump 32 is rotatable in the forward and reverse directions. Specifically, the forward rotation direction is a direction in which oil is supplied to the PRI pulley oil chamber 21c side, and the reverse direction is a direction in which the oil is supplied to the SEC pulley oil chamber 22c side.

  The switching valve 36 is provided in a portion of the first oil passage R1 between the electric oil pump 32 and the PRI pulley oil chamber 21c. The switching valve 36 includes a first position P1 and a second position P2 as a switching position, and is configured to be able to switch the first position P1 and the second position P2. The switching position of the switching valve 36 will be described later.

  The electric oil pump 32 communicates with the oil reservoir 37 through the second oil passage R2. Specifically, the second oil passage R2 is connected to a strainer 37a in the oil reservoir 37. The second oil passage R2 includes an oil passage communicating the oil reservoir 37 with the switching valve 36, and a portion of the first oil passage R1 between the switching valve 36 and the electric oil pump 32. The former oil passage is an oil passage not passing through another oil passage connected to the switching valve 36. As a result of the switching valve 36 being provided to connect these, it is further provided in the second oil passage R2.

  Specifically, the second oil passage R2 is connected to the oil inlet / outlet 32a on the side of the PRI pulley oil chamber 21c of the electric oil pump 32. The portion of the first oil passage R1 between the switching valve 36 and the electric oil pump 32 doubles as a part of the second oil passage R2. The mechanical oil pump 31 is also connected to a portion of the second oil passage R2 closer to the oil reservoir 37 than the switching valve 36 via the suction side oil passage Rin.

  Such a second oil passage R2 and the switching valve 36 can be grasped as follows. That is, the second oil passage R2 can be grasped as an oil passage which branches from the first oil passage R1 between the electric oil pump 32 and the PRI pulley oil chamber 21c and communicates with the oil reservoir 37. Further, the switching valve 36 can be grasped as a switching valve provided at a branch point of the first oil passage R1 and the second oil passage R2.

  The oil reservoir 37 is an oil reservoir for storing oil supplied by the mechanical oil pump 31 and the electric oil pump 32. The oil is sucked from the oil reservoir 37 via the strainer 37a. The oil reservoir 37 may be composed of a plurality of oil reservoirs.

Electric oil pump 32, the clutch 40 by the clutch oil passage _{R CL,} specifically communicates with the clutch oil chamber 40a of the clutch 40. The clutch oil passage _RCL includes a portion of the first oil passage R1 between the electric oil pump 32 and the second point C2. The second point C2 is a point on the first oil passage R1 between the electric oil pump 32 and the first point C1. The clutch oil passage _RCL further includes an oil passage connecting the second point C2 and the clutch 40.

Specifically, the clutch oil passage R _CL is connected to the oil inlet / outlet 32 b on the SEC pulley oil chamber 22 c side of the electric oil pump 32. A portion between the electric oil pump 32 and the second point C2 of the first oil passage R1 also serves as a part of the clutch oil passage R _CL. The clutch oil passage _RCL is an oil passage not passing through the second oil passage R2.

  The clutch 40 is engaged by supplying oil to the clutch oil chamber 40a, and released by draining oil from the clutch oil chamber 40a. The clutch 40, together with the variator 2, transmits power between the engine ENG and the drive wheels. The clutch 40 connects and disconnects a power transmission path connecting the engine ENG and the drive wheels. The clutch 40 constitutes a hydraulic device other than the variator 2.

A pilot valve 38 is provided at a portion of the clutch oil passage _RCL branched from the first oil passage R1. A clutch pressure solenoid 39 is provided in a portion of the clutch oil passage _RCL between the pilot valve 38 and the clutch 40. The pilot valve 38 depressurizes the oil supplied from the first oil passage R1. The clutch pressure solenoid 39 adjusts the hydraulic pressure supplied to the clutch 40, that is, the hydraulic pressure P _CL of the clutch oil chamber 40a.

A PRI oil passage R _PRI further branches from the clutch oil passage R _CL and communicates with the PRI pulley oil chamber 21 c. PRI oil passage R _PRI includes an oil passage connecting the clutch oil passage R _CL and the switching valve 36, and a portion of the first oil passage R1 between the switching valve 36 and the PRI pulley oil chamber 21c. The former oil passage is an oil passage not passing through another oil passage connected to the switching valve 36. As a result of the switching valve 36 being provided to connect these, it is further provided in the PRI oil passage _RPRI .

Specifically, the PRI oil passage R _PRI branches from a portion of the clutch oil passage R _CL between the clutch pressure solenoid 39 and the clutch 40. The portion of the first oil passage R1 between the PRI pulley oil chamber 21c and the switching valve 36 also serves as part of the fourth oil passage R4.

Such PRI oil passage R _PRI together with a part of the clutch oil passage R _CL (specifically, the clutch oil passage R _CL between the second point C 2 and the point where the PRI oil passage R _PRI branches) It can be grasped as a third oil passage R3 which branches from the first oil passage R1 between the pump 32 and the SEC pulley oil chamber 22c and reaches the switching valve 36.

In addition, the hydraulic circuit 3, part of the oil passage connecting branches to the line pressure solenoid 35 and T / C hydraulic system 41 between the pilot valve 38 and the clutch pressure solenoid 39 of the clutch fluid passage R _CL Each is provided.

  The line pressure solenoid 35 generates a solenoid pressure according to the command value of the line pressure PL, and supplies the solenoid pressure to the line pressure adjustment valve 34. The T / C hydraulic system 41 is a hydraulic system of the torque converter TC including the lockup clutch LU, and the oil drained from the line pressure adjusting valve 34 is also supplied to the T / C hydraulic system 41.

  In the hydraulic circuit 3 configured as described above, the mechanical oil pump 31 supplies the SEC pressure Psec to the SEC pulley oil chamber 22c, and the electric oil pump 32 controls oil in and out of the PRI pulley oil chamber 21c. The mechanical oil pump 31 is used to hold the belt 23, and the electric oil pump 32 is used to shift.

  That is, as the shifting principle, shifting is performed by moving the oil from one of the PRI pulley oil chamber 21c and the SEC pulley oil chamber 22c to the other by the electric oil pump 32.

  The vehicle is further provided with a controller 10. The controller 10 is configured to have a transmission controller 11 and an engine controller 12.

  The transmission controller 11 includes a rotation sensor 51 for detecting the rotation speed on the input side of the variator 2, a rotation sensor 52 for detecting the rotation speed on the output side of the variator 2, and an oil pressure of the PRI pulley oil chamber 21c. Signals from the pressure sensor 53 for detecting the PRI pressure Ppri and the pressure sensor 54 for detecting the SEC pressure Psec are input. Specifically, rotation sensor 51 detects rotational speed Npri of PRI pulley 21. The rotation sensor 52 specifically detects the rotational speed Nsec of the SEC pulley 22. The transmission controller 11 can detect the vehicle speed VSP based on the input from the rotation sensor 52.

  Further, signals from an accelerator opening degree sensor 55, a brake sensor 56, a selection range detection switch 57, an engine rotation sensor 58, an oil temperature sensor 59, and an oil pressure sensor 60 are input to the transmission controller 11.

An accelerator opening degree sensor 55 detects an accelerator opening degree APO that represents an operation amount of an accelerator pedal. The brake sensor 56 detects a brake pedal depression force BRK. The selection range detection switch 57 detects the range RNG selected by the shift lever which is a selector. Engine rotation sensor 58 detects rotation speed Ne of engine ENG. The oil temperature sensor 59 detects the oil temperature T _OIL of the transmission 1. The oil temperature T _OIL is the temperature of the oil used as the hydraulic oil in the variator 2. The hydraulic pressure sensor 60 detects the hydraulic pressure P _CL .

  The transmission controller 11 is communicably connected to the engine controller 12. Engine torque information Te is input to the transmission controller 11 from the engine controller 12. Signals from the accelerator opening sensor 55 and the engine rotation sensor 58 may be input to the transmission controller 11 via the engine controller 12, for example.

  The transmission controller 11 generates a control signal including a transmission control signal based on the input signal, and outputs the generated control signal to the hydraulic circuit 3. In the hydraulic circuit 3, the electric oil pump 32, the line pressure solenoid 35, the switching valve 36, the clutch pressure solenoid 39 and the like are controlled based on the control signal from the transmission controller 11. Thus, for example, the transmission ratio of the variator 2 is controlled to the transmission ratio corresponding to the transmission control signal, that is, the target transmission ratio.

  In addition to this, the transmission controller 11 performs, for example, select control that switches the clutch 40 between the engaged state and the released state when the driver performs a select operation. The selection operation includes the selection operation for switching the clutch 40 from the released state to the engaged state. When the clutch 40 is a reverse brake, such a selection operation is specifically, for example, an R range selection operation from the D range.

  In the present embodiment, the controller 10 configured to have the transmission controller 11 and the engine controller 12 constitutes a power transmission device together with the transmission 1. The transmission controller 11 is configured to perform the above-described select control, and is configured to have a clutch control unit.

  Next, the switching position of the switching valve 36 will be described.

  2A and 2B are explanatory diagrams of the switching position of the switching valve 36. FIG. FIG. 2A shows the switching position, that is, the case where the valve position is the first position P1, and FIG. 2B shows the case where the switching position is the second position P2.

As shown in FIG. 2A, the first position P1 is a switching position where the first oil passage R1 is in the communication state and the second oil passage R2 is in the blocking state. Further, at the first position P1, the PRI oil passage R _PRI is brought into the shutoff state. As a result, in the case of the first position P1, the mechanical oil pump 31 supplies the oil of the oil reservoir 37 to the SEC pulley oil chamber 22c and the clutch 40, and the electric oil pump 32 controls the oil in and out of the PRI pulley oil chamber 21c. Do.

As shown in FIG. 2B, the second position P2 is a switching position where the first oil passage R1 is in the closed state and the second oil passage R2 is in the communication state. At the second position P2, the PRI oil passage R _PRI is further brought into communication. As a result, in the case of the second position P2, the electric oil pump 32 is in communication with the clutch 40 and the PRI pulley oil chamber 21c, and supplies the oil of the oil reservoir 37 to the clutch 40 and the PRI pulley oil chamber 21c.

Further in the case of the second position P2, it is possible to supply to the PRI pulley oil chamber 21c and by regulating the oil in the clutch oil passage R _CL clutch pressure solenoid 39. Therefore, even if the first oil passage R1 is shut off by the switching valve 36, the variator 2 can be shifted.

Clutch pressure solenoid 39 is configured to constitute the oil regulating pressure regulating valve is supplied to the clutch 40, which constitutes a pressure regulating of adjusting the hydraulic pressure of the PRI oil passage R _PRI. The PRI oil passage R _PRI and the clutch pressure solenoid 39 constitute a PRI pressure supply unit capable of adjusting the oil in the clutch oil passage R _CL and supplying it to the PRI pulley oil chamber 21 c.

By the PRI oil passage _{R PRI} and the clutch pressure solenoid 39 which constitutes the PRI pressure supply unit, the oil in the clutch oil passage _{R CL} is pressure regulated to a predetermined fluid pressure PA. The predetermined hydraulic pressure PA is, for example, an instruction pressure of the PRI pressure Ppri, and the PRI pressure Ppri supplied at the time of the shift is larger than the engagement pressure of the clutch 40. Therefore, in the second position P2, the shift of the variator 2 can be performed while the clutch 40 is in the engaged state.

  Such a switching valve 36 can be grasped as follows in addition to the fact that the second oil passage R2 and the switching valve 36 can be grasped as described above. That is, the switching valve 36 brings the first position P1 in which at least the first oil passage R1 into communication state, the second oil passage R2 and the SEC pulley oil chamber 22c side of the first oil passage R1 into communication with each other. It can be grasped as a switching valve which switches two positions of 3 oil passage R3 and the 2nd position P2 which makes the PRI pulley oil chamber 21c side of 1st oil passage R1 a communication state.

  Next, the relationship between the supply flow rate Qmp, which is the supply flow rate of oil of the mechanical oil pump 31, and the required flow rate Qsel, which is the flow rate of oil required for select control, will be described.

  FIG. 3 is a view for explaining the relationship between the supply flow rate Qmp and the required flow rate Qsel. In FIG. 3, the supply flow rate Qmp ′, which is the supply flow rate Qmp in the case of the comparative example, is also shown. The comparative example is a case where the gear is supplied by supplying oil to the PRI pulley oil chamber 21c by the mechanical oil pump 31 and adjusting the oil supplied to the PRI pulley oil chamber 21c by the pressure control valve. The required flow rate Qsel and the required flow rate Qv of oil required for the variator 2 indicate the flow rate of the mechanical oil pump 31.

  The required flow rate Qv includes the pressure securing required flow rate Qv1 necessary for preventing the slip of the belt 23, and the shift required flow rate Qv2 necessary for shifting. In the case of the present embodiment, since the electric variable oil pump 32 performs the shift of the variator 2, the electric current required pump flow rate Qv 2 is covered by the electric oil pump 32. Therefore, in the present embodiment, it is possible to miniaturize the mechanical oil pump 31 because the necessary flow rate Qv2 for shifting is unnecessary as compared with the comparative example.

  However, in the scene selected by the driver, the rotational speed Ne is low and the rotational speed Nep of the mechanical oil pump 31 is also low. Therefore, if the mechanical oil pump 31 is miniaturized, there is a concern that the supply flow rate Qmp may be insufficient for the required flow rate Qsel. Specifically, in the present embodiment, as the supply flow rate Qmp_idl during idle operation of the engine ENG becomes smaller than the required flow rate Qsel, the supply flow rate Qmp runs short with respect to the required flow rate Qsel.

  In view of such circumstances, in the present embodiment, the controller 10 performs the control described below.

  FIG. 4 is a flowchart showing an example of control performed by the controller 10. Specifically, the process of this flowchart can be configured to be performed by the transmission controller 11.

  In step S1, the controller 10 determines whether or not the oil amount balance of the mechanical oil pump 31 is insufficient for the required flow rate Qsel. In other words, in step S1, it is determined whether the supply flow rate Qmp is smaller than the required flow rate Qsel.

The determination in step S1 is specifically, the oil temperature T _OIL is equal to or higher than a predetermined temperature TA, and the rotational speed Ne is carried out by determining whether or not less than a predetermined rotational speed Ne1. The predetermined temperature TA and the predetermined rotation speed Ne1 are determination values for determining whether the supply flow rate Qmp is smaller than the required flow rate Qsel, and are set in advance. If it is affirmation determination by step S1, a process will progress to step S2.

  In step S2, the controller 10 determines whether or not selection control is in progress. For example, it can be determined based on the output of the selection range detection switch 57 whether the selection control is being performed. If a negative determination is made in step S1 or step S2, the process returns to step S1. If the determination in step S2 is affirmative, the process proceeds to step S3 and further to step S4.

  In steps S3 and S4, first transition control is performed to shift the control state from the first control state in which the electric oil pump 32 performs shift control to the second control state in which the electric oil pump 32 controls oil supply. The electric oil pump 32 controls the oil in and out of the PRI pulley oil chamber 21c in the shift control, and supplies the oil in the direction to supply the oil to the clutch oil chamber 40a in the oil supply control.

  Specifically, the controller 10 sets the switching position of the switching valve 36 to the second position P2 in step S3. Further, at step S4, the controller 10 performs oil supply control by the electric oil pump 32.

  Specifically, in step S4, the rotational direction of the electric oil pump 32 is changed from the normal direction to the reverse direction. Further, the supply flow rate Qep of the electric oil pump 32 is set to the flow rate Qep2 which is equal to or higher than the flow rate of the oil which is insufficient in the select control.

  The supply flow rate Qep does not distinguish positive or negative depending on the rotation direction of the electric oil pump 32, and represents an absolute value. Specifically, the supply flow rate Qep is changed from the flow rate Qep1 smaller than the flow rate of the oil lacking in the select control to the flow rate Qep2. The flow rate of the oil which is insufficient in the select control can be calculated as the flow rate of the electric oil pump 32 based on the required flow rate Qsel and the supply flow rate Qmp.

  In step S5, the controller 10 determines whether the select control has ended. For example, it can be determined based on the output of the hydraulic pressure sensor 60 whether the selection control has ended. For example, it may be determined whether or not the differential rotation of the clutch 40 has become equal to or less than a predetermined value. If a negative determination is made in step S5, the process returns to step S5. If the determination in step S5 is affirmative, the process proceeds to step S6 and further to step S7.

  In steps S6 and S7, the second transition control is performed to shift the control state from the second control state in which the oil supply control is performed by the electric oil pump 32 to the first control state in which the shift control is performed by the electric oil pump 32.

  Specifically, in step S6, the controller 10 sets the switching position of the switching valve 36 to the first position P1. Further, at step S7, the controller 10 performs shift control by the electric oil pump 32.

  Specifically, in step S7, the rotation direction of the electric oil pump 32 is changed from the reverse rotation direction to the normal rotation direction. Further, the supply flow rate Qep of the electric oil pump 32 is set to the flow rate Qep1. After step S7, the process of this flowchart is temporarily ended.

  The controller 10 is configured to execute the process of step S7, and is configured to have an oil pump control unit. The process corresponding to the oil pump control unit further includes the process of step S4.

  The controller 10 is configured to execute the process of step S3, and is configured to have a switching valve control unit. The process corresponding to the switching valve control unit further includes the process of step S6. The controller 10 is configured to execute the processes of step S1, step S2, and step S5, and is configured to have a determination unit that performs the corresponding process among these processes.

FIG. 5 is a diagram showing an example of a timing chart corresponding to the flowchart shown in FIG. In Figure 5, at a predetermined temperature TA or the oil temperature T _OIL, it shows a case where the R range select operation from the D-range is performed. The rotational speed Nt indicates the turbine rotational speed of the torque converter TC.

  At timing T1, the rotational speed Ne becomes equal to or lower than the predetermined rotational speed Ne1 during decelerating travel in the D range. Therefore, at timing T1, it is determined that the oil amount balance of the mechanical oil pump 31 is insufficient with respect to the required flow rate Qsel.

  Immediately before timing T2, the lockup clutch LU is released, and at timing T2, the vehicle stops. As a result, the rotational speed Ne and the rotational speed Nt both become steady. Specifically, the rotational speed Ne becomes the idle rotational speed Ne2, and the rotational speed Nt becomes zero.

  At timing T3, the range RNG is changed from the D range to the R range by the selection operation. At timing T3, the selection control is considered to be started by the selection operation, and the selection control is actually started.

  As a result, the switching position of the switching valve 36 is changed from the first position P1 to the second position P2. Further, the rotational speed Nep of the electric oil pump 32 is changed from the positive rotational speed Nep1 to the negative rotational speed Nep2. The rotational speed Nep1 is a rotational speed Nep corresponding to the flow rate Qep1, and the rotational speed Nep2 is a rotational speed Nep corresponding to the flow rate Qep2. At timing T3, the use of the electric oil pump 32 is switched from gear change to oil supply by changing the switching position of the switching valve 36 and the rotational speed Nep.

  During the select control, switching of the frictional engagement element from the forward clutch to the clutch 40 serving as the reverse brake is performed. At this time, the forward clutch and the clutch 40 are temporarily released, and in the torque converter TC, the turbine is engaged with the rotation of the engine ENG and tries to rotate. As a result, the rotational speed Nt rises toward the rotational speed Ne. The rotational speed Nt then converges to zero as the engagement of the clutch 40 proceeds.

  At timing T4, the rotational speed Nt becomes zero again by the engagement of the clutch 40, and the selection control ends. As a result, the switching position of the switching valve 36 is changed from the second position P2 to the first position P1. Further, the rotational speed Nep is changed from the negative rotational speed Nep2 to the positive rotational speed Nep1. At timing T4, these changes cause the application of the electric oil pump 32 to return from the oil supply to the shift. Thereafter, at timing T5, the vehicle starts moving in the R range and the rotational speed Ne and the rotational speed Nt begin to increase, and at timing T6, the rotational speed Ne exceeds the predetermined rotational speed Ne1.

  Next, main operational effects of the power transmission device according to the present embodiment will be described.

  The power transmission device according to the present embodiment includes a variator 2 and a clutch 40, and an electric oil pump 32. The power transmission device includes the controller 10 configured to control the entry and exit of oil in the PRI pulley oil chamber 21c by the electric oil pump 32 and configured to perform select control when the driver performs a select operation. . The controller 10 is configured to supply oil to the clutch oil chamber 40a by the electric oil pump 32 during select control.

  According to such a configuration, in addition to the mechanical oil pump 31, the electric oil pump 32 can supply necessary oil in selection control. Therefore, even if the mechanical oil pump 31 is downsized in combination with the speed change of the variator 2 by the electric oil pump 32, the necessary oil can be supplied by the select control (effects corresponding to claims 1 and 9).

  The power transmission device according to the present embodiment further includes a second oil passage R2, a third oil passage R3, and a switching valve 36. According to such a configuration, it is possible to supply the oil to the clutch 40 by the electric oil pump 32 which performs a shift (effect corresponding to claim 2).

  The power transmission device according to the present embodiment further includes a mechanical oil pump 31. In the present embodiment, the controller 10 is configured to switch the switching position of the switching valve 36 from the first position P1 to the second position P2 when it is determined that the supply flow rate Qmp is insufficient for the required flow rate Qsel. Be done.

  According to such a configuration, it is possible to supply oil to the clutch 40 by the electric oil pump 32 in accordance with the selection control (an effect corresponding to claim 3).

  In the present embodiment, even if it is determined that the supply flow rate Qmp is insufficient for the required flow rate Qsel, the controller 10 moves the switching position of the switching valve 36 to the first position P1 until it is considered that the select control is started. maintain.

  According to such a configuration, since the switching position of the switching valve 36 is maintained at the first position P1 until it is considered that the selection control is started, unnecessary switching of the switching valve 36 is not performed. (Effect corresponding to claim 4).

  In the present embodiment, the supply flow rate Qmp_idl is smaller than the required flow rate Qsel. The power transmission apparatus is effective in such a configuration in supplying the oil required for the select control (effect corresponding to claim 8).

Second Embodiment
FIG. 6 is a flowchart showing an example of control performed by the controller 10 in the second embodiment. In the power transmission device according to the present embodiment, the controller 10 is configured to perform the processing of this flowchart. The same processing as the processing of the flowchart shown in FIG. 4 is assigned the same reference numeral, and in the following, portions different from the flowchart shown in FIG. 4 will be mainly described.

  In the second embodiment, if it is determined in step S1 that the oil amount balance is insufficient, the process proceeds to step S3 and further to step S4. That is, in the second embodiment, when it is determined that the oil amount balance is insufficient, the first transition control is performed regardless of whether the select control is in progress. As a result, before the selection control is considered to be started, the first transition control is performed. After step S4, the process proceeds to step S11.

  In step S11, the controller 10 determines whether or not there is a select operation. If an affirmative determination is made in step S11, it is considered that select control has been started. In this case, the process proceeds to step S12.

  In step S12, the controller 10 starts select control. After step S12, the process proceeds to step S13. Also in the case of a negative determination in step S11, the process proceeds to step S13.

  In step S13, the controller 10 determines whether the oil amount balance of the mechanical oil pump 31 is sufficient for the required flow rate Qsel. The determination in step S13 is a determination in which the positive determination and the negative determination are reversed with respect to the determination in step S1.

  If a negative determination is made in step S13, the process returns to step S11. As a result, oil supply control by the electric oil pump 32 is continued until the oil amount balance of the mechanical oil pump 31 is sufficient. If it is affirmation determination by step S13, a process will progress to step S6 and also step S7. That is, in the second embodiment, the second transition control is performed after the oil amount balance is determined to be sufficient. After step S18, the process of this flowchart is temporarily ended.

  FIG. 7 is a diagram showing an example of a timing chart corresponding to the flowchart shown in FIG. In the following, portions different from the timing chart shown in FIG. 5 will be mainly described.

  In the second embodiment, when it is determined that the oil amount balance of the mechanical oil pump 31 is insufficient at timing T1, the switching position of the switching valve 36 is changed from the first position P1 to the second position P2, and the rotational speed Nep is The positive rotational speed Nep1 is changed to the negative rotational speed Nep2. As a result, the rotation direction of the electric oil pump 32 is changed to the reverse direction, that is, the direction in which the oil is supplied to the clutch oil chamber 40a, and the supply flow rate Qep is set to the flow rate Qep2.

  In the second embodiment, when it is determined that the oil amount balance of the mechanical oil pump 31 is sufficient at the timing T6, the switching position of the switching valve 36 is changed from the second position P2 to the first position P1 and rotation The speed Nep is changed from the negative rotation speed Nep2 to the positive rotation speed Nep1. As a result, the rotation direction of the electric oil pump 32 is changed to the normal rotation direction, that is, the direction in which the oil is supplied to the PRI pulley oil chamber 21c, and the supply flow rate Qep is set to the flow rate Qep1.

  The change of the rotational direction of the electric oil pump 32 and the supply flow rate Qep performed at the timing T1 can be performed, for example, after the predetermined time set in advance from the timing T2 or the timing T1 or the timing T2.

  It is also possible to change the rotational direction of the electric oil pump 32 and the supply flow rate Qep performed at the timing T6 after the timing T4, that is, after the end of the select control.

  Furthermore, the change of the supply flow rate Qep can be performed after the change of the rotational direction of the electric oil pump 32 is performed.

  As described above, in the second embodiment, when it is determined that the supply flow rate Qmp is insufficient relative to the required flow rate Qsel, the controller 10 determines the switching position of the switching valve 36 before it is considered that the select control is started. It is configured to switch from the first position P1 to the second position P2.

  According to such a configuration, since the switching position of the switching valve 36 can be switched in preparation for selection control, it is possible to prevent switching delay of the switching valve 36 from occurring with respect to the selection control (claim 5) Corresponding effect).

  In the second embodiment, when it is determined that the supply flow rate Qmp is insufficient for the required flow rate Qsel, the controller 10 reverses the rotational direction of the electric oil pump 32 before it is considered that the select control has been started. That is, the clutch oil chamber 40a is changed to the direction in which the oil is supplied, and the supply flow rate Qep is set to the flow rate Qep2.

  According to such a configuration, since oil supply control can be performed by the electric oil pump 32 in preparation for select control, it is possible to prevent a delay in oil supply from the electric oil pump 32 with respect to the select control. Yes (effect corresponding to claim 6).

Third Embodiment
FIG. 8 is a flowchart showing an example of control performed by the controller 10 in the third embodiment. In the power transmission device according to the present embodiment, the controller 10 is configured to perform the processing of this flowchart. The same processing as the processing of the flowchart shown in FIG. 6 is assigned the same reference numeral, and in the following, portions different from the flowchart shown in FIG. 6 will be mainly described.

  In the third embodiment, when it is determined in step S1 that the oil amount balance is insufficient, the controller 10 sets the supply flow rate Qep to the flow rate Qep1 in step S4 ′ following step S3. That is, in the third embodiment, in the oil supply control by the electric oil pump 32, the rotational direction is changed to the reverse direction as in the second embodiment, while the supply flow rate Qep is left as it is.

  After step S4 ', the process proceeds to step S11. In addition, if the affirmative judgment is made in Step S11 and it is considered that the selection control is started, the process proceeds to Step S12 '.

  In step S12 ', the controller 10 starts select control, and sets the supply flow rate Qep to the flow rate Qep2. That is, in the third embodiment, when it is considered that the select control is started, the supply flow rate Qep is set to the flow rate Qep2.

  In step S121 following step S12 ', the controller 10 determines whether the selection control has ended. If the determination in step S121 is negative, the process returns to step S121. If the determination in step S121 is affirmative, the process proceeds to step S122.

  In step S122, the controller 10 sets the supply flow rate Qep to the flow rate Qep1. That is, in the third embodiment, when the selection control ends, the supply flow rate Qep is set to the flow rate Qep1 regardless of whether the oil amount balance is sufficient. As a result, the power consumption of the electric oil pump 32 is suppressed. After step S122, the process proceeds to step S13.

  FIG. 9 is a diagram showing an example of a timing chart corresponding to the flowchart shown in FIG. In the following, portions different from the timing chart shown in FIG. 7 will be mainly described.

  In this example, the rotational speed Nep is changed from the positive rotational speed Nep1 to the negative rotational speed Nep1 ′ at timing T1 at which it is determined that the oil amount balance is insufficient. The rotational speed Nep1 'corresponds to the flow rate Qep1 as the rotational speed Nep1.

  In this example, the rotational speed Nep is set to the negative rotational speed Nep2 at timing T3 at which select control is started. Furthermore, in this example, the rotational speed Nep is set to the negative rotational speed Nep1 'at timing T4 when the selection control ends. The rotational speed Nep is set to the rotational speed Nep1 at timing T6 when it is determined that the oil amount balance is sufficient.

  Thus, in the third embodiment, when it is determined that the supply flow rate Qmp is insufficient for the required flow rate Qsel, the controller 10 rotates the electric oil pump 32 before it is considered that the select control has been started. The direction is changed to the reverse direction, that is, the direction in which the oil is supplied to the clutch oil chamber 40a, and the supply flow rate Qep is set to the flow rate Qep1. On the other hand, when it is considered that the select control has been started, the controller 10 sets the supply flow rate Qep to the flow rate Qep2.

  According to such a configuration, by setting the supply flow rate Qep to the flow rate Qep1 and the flow rate Qep2 in stages, it is possible to make it difficult to cause delay in oil supply from the electric oil pump 32 as compared with the first embodiment. As compared with the second embodiment, power consumption can be suppressed (an effect corresponding to claim 7).

  As mentioned above, although the embodiment of the present invention was described, the above-mentioned embodiment showed only a part of application example of the present invention, and in the meaning of limiting the technical scope of the present invention to the concrete composition of the above-mentioned embodiment. Absent.

  In the embodiment described above, the case where the clutch 40 is a reverse brake engaged in the R range and the selection operation is the R range selection operation from the D range has been described.

  However, the clutch 40 may be any clutch that is engaged by select control, and may be, for example, a forward clutch that is engaged when the D range is selected. In addition to the selection operation between D range and R range, select operation is an operation to select a travel range including D range and R range from P range, that is, parking range and N range, that is, non-traveling range including neutral range. It may be

  In the select operation between the D range and the R range, that is, the select operation in which the frictional engagement element is switched, the release hydraulic pressure to the release side clutch needs to be maintained because the release control of the release side clutch is necessary. Therefore, in this case, as the required flow rate Qsel increases by that much, the problem that the required flow rate Qsel exceeds the supply flow rate Qmp is more likely to occur than in the case of the travel range selection operation from the non-traveling range.

  In the embodiment described above, the case where the controller 10 including the transmission controller 11 and the engine controller 12 performs control has been described. However, a single controller, such as, for example, the transmission controller 11, may be configured to provide control.

1 Transmission 2 Variator (continuously variable transmission mechanism)
21c PRI pulley oil chamber 22c SEC pool oil chamber 3 hydraulic circuit 31 mechanical oil pump 32 electric oil pump 36 switching valve 37 oil reservoir (oil reservoir)
39 clutch pressure solenoid 40 clutch 40a clutch oil chamber 10 controller (oil pump control unit, clutch control unit, switching valve control unit)
11 Transmission controller (oil pump control unit, clutch control unit, switching valve control unit)
12 Engine Controller ENG Engine R1 1st oil path R2 2nd oil path R3 3rd oil path R _CL clutch oil path (3rd oil path)
R _PRI PRI oil passage (third oil passage)

Claims (9)

A continuously variable transmission mechanism and a clutch for transmitting power between a drive source and a driving wheel, and a first oil passage communicating the primary pulley oil chamber and the secondary pulley oil chamber of the continuously variable transmission mechanism And an electric oil pump configured to be able to supply the oil of the first to the clutch oil chamber which is the oil chamber of the clutch.
An oil pump control unit configured to control oil in and out of the primary pulley oil chamber by the electric oil pump;
A clutch control unit that performs select control that switches the clutch between a engaged state and a released state when the driver performs a select operation;
Equipped with
The oil pump control unit supplies oil to the clutch oil chamber by the electric oil pump during the select control.
Power transmission device characterized by The power transmission device according to claim 1,
A second oil passage branched from the first oil passage between the electric oil pump and the primary pulley oil chamber and communicating with an oil reservoir;
A switching valve provided at a branch point between the first oil passage and the second oil passage;
A third oil passage branched from the first oil passage between the electric oil pump and the secondary pulley oil chamber and reaching the switching valve;
And further
The switching valve is
A first position in which at least the first oil passage is in communication;
The second oil passage is in communication with the secondary pulley oil chamber side of the first oil passage, and the third oil passage is in communication with the primary pulley oil chamber side of the first oil passage. Switch between 2 positions, 2 positions,
Power transmission device characterized by The power transmission device according to claim 2,
It further comprises a mechanical oil pump driven by the drive source and configured to be able to supply the oil of the oil reservoir to the secondary pulley oil chamber and the clutch oil chamber.
A switching valve control unit that switches the switching position of the switching valve from the first position to the second position when it is determined that the supply flow rate of the mechanical oil pump is insufficient relative to the flow rate required for the select control;
And a power transmission device. The power transmission device according to claim 3,
The switching valve control unit switches the switching valve until it is considered that the selection control has been started even if it is determined that the supply flow rate of the mechanical oil pump is insufficient relative to the necessary flow of the selection control. Maintaining a position at said first position,
Power transmission device characterized by The power transmission device according to claim 3,
When it is determined that the supply flow rate of the mechanical oil pump is insufficient relative to the required flow rate of the select control, the change-over valve control unit is configured to determine whether the change control is started before the select control is started. Switching the switching position from the first position to the second position;
Power transmission device characterized by The power transmission device according to claim 5, wherein
When it is determined that the supply flow rate of the mechanical oil pump is insufficient relative to the required flow rate of the select control, the oil pump control unit is configured to determine the electric oil pump before the select control is started. Changing the rotation direction of the electric motor to the direction in which the oil is supplied to the clutch oil chamber, and setting the supply flow rate of the electric oil
Power transmission device characterized by The power transmission device according to claim 5, wherein
The oil pump control unit determines that the supply flow rate of the mechanical oil pump is insufficient relative to the required flow rate of the select control,
Before it is considered that the select control is started, the rotation direction of the electric oil pump is changed to a direction for supplying oil to the clutch oil chamber, and the supply flow rate of the electric oil pump is insufficient in the select control. While setting the flow rate smaller than the oil flow rate,
When it is considered that the select control has been started, the supply flow rate of the electric oil pump is set to a flow rate equal to or higher than the flow rate of the oil which is insufficient in the select control,
Power transmission device characterized by The power transmission device according to any one of claims 3 to 7, wherein
The supply flow rate of the mechanical oil pump during idle operation of the drive source is smaller than the flow rate of oil required by the select control,
Power transmission device characterized by A continuously variable transmission mechanism and a clutch for transmitting power between a drive source and a driving wheel, and a first oil passage communicating the primary pulley oil chamber and the secondary pulley oil chamber of the continuously variable transmission mechanism A control method of a power transmission device, comprising: an electric oil pump configured to be able to supply the oil of the second embodiment to a clutch oil chamber which is an oil chamber of the clutch.
Controlling oil in and out of the primary pulley oil chamber with the electric oil pump;
Performing select control to switch the clutch between the engaged state and the released state when selected by the driver;
Including
While the entry and exit of oil in the primary pulley oil chamber is controlled by the electric oil pump, oil is supplied to the clutch oil chamber by the electric oil pump during the select control.
And controlling the power transmission device.

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