JP6502692B2 - Hydraulic pressure supply device and control method of hydraulic pressure supply device - Google Patents

Description

  The present invention relates to a hydraulic pressure supply device and a control method of the hydraulic pressure supply device.

  The vehicle is provided with a transmission for transmitting the output torque of an engine or drive motor as a drive source to drive wheels in accordance with the traveling state of the vehicle. As one aspect of such a transmission, there is a belt type automatic transmission in which a groove width of a pulley around which a belt is wound is changed by hydraulic pressure. The belt type automatic transmission includes a primary pulley to which an output torque of a drive source is transmitted, a secondary pulley which changes and outputs an output torque transmitted to the primary pulley, and a belt wound around the primary pulley and the secondary pulley. Prepare.

  In the belt type automatic transmission, the ratio of the output torque transmitted to the primary pulley and the output torque output from the secondary pulley is changed by changing the groove width of the secondary pulley by the hydraulic pressure. In such a belt type automatic transmission, the output torque is controlled by controlling the hydraulic pressure supplied to each hydraulic pressure chamber with a pressure control valve while supplying the hydraulic fluid discharged by the oil pump to the hydraulic pressure chambers of the primary pulley and the secondary pulley. The ratio of

  By the way, in recent years, when the vehicle stops at an intersection etc. while driving the vehicle, the engine is automatically stopped with the establishment of the automatic stop condition and the engine is restarted with the establishment of the restart condition (hereinafter referred to as “idling stop control It is also put to practical use. The idling stop control is control for automatically stopping the engine while the vehicle is stopped while the key switch of the engine is on, and fuel efficiency can be improved.

  An oil pump that supplies hydraulic pressure to the above-described automatic transmission is generally driven by the driving force of the engine. Therefore, during the automatic stop of the engine by the idling stop control, the supply of hydraulic pressure to the automatic transmission is stopped. During this time, the hydraulic pressure gradually decreases as the hydraulic oil leaks in the hydraulic circuit. The hydraulic circuit of an automatic transmission is generally shared with a hydraulic circuit that supplies hydraulic fluid to other hydraulic devices such as a torque converter. Therefore, during the automatic stop of the engine, the hydraulic pressures of the other hydraulic devices also gradually decrease.

  On the other hand, Patent Document 1 includes an accumulator for accumulating hydraulic fluid, and supplies hydraulic fluid to an automatic transmission by an oil pump driven by a power source different from the engine during automatic stop of the engine. In addition, a hydraulic pressure supply device is disclosed that supplies hydraulic fluid accumulated in an accumulator to a clutch device when the engine is restarted. According to the patent document 1, the clutch device can be quickly engaged when the engine is restarted while preventing the oil pressure of the automatic transmission from being lowered during the automatic stop of the engine by the idling stop control. In patent document 1, it is comprised so that a part of hydraulic fluid discharged by the oil pump may be accumulated in an accumulator.

JP, 2010-216643, A

  However, the hydraulic pressure supply device described in Patent Document 1 accumulates part of the hydraulic fluid discharged by the oil pump when the pressure of the hydraulic fluid in the accumulator is lower than the lower limit value. Therefore, if the consumption flow rate of the hydraulic fluid in the automatic transmission increases until the accumulation of pressure in the accumulator is completed, there is a risk that the supply of hydraulic fluid to the automatic transmission may be insufficient. In particular, the consumption flow rate of the hydraulic oil in the automatic transmission increases in the low speed range immediately after engine start, and the flow rate balance becomes severe, but in the hydraulic pressure supply device of Patent Document 1, the pressure accumulation in the accumulator is completed in this period. If not, it is not possible to stably supply the hydraulic pressure to the automatic transmission.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide an accumulator that enables stable supply of hydraulic fluid to a hydraulic circuit regardless of the rotation range of the oil pump. It is an object of the present invention to provide a hydraulic pressure supply device and a control method of the hydraulic pressure supply device, capable of accumulating pressure.

In order to solve the above problems, according to one aspect of the present invention, a drive rotor having external teeth, and a driven rotor having internal teeth and meshed with the drive rotor are driven by the driving force of an engine. The hydraulic fluid is introduced through the suction port and the hydraulic pressure through the discharge port by the volume change of the pump chamber formed between the drive rotor and the driven rotor with the rotation of the drive rotor and the driven rotor. An oil pump for discharging the hydraulic fluid to a circuit; and a pressure leak port communicating with the pump chamber at a position before communication between the pump chamber and the discharge port after disconnection between the pump chamber and the suction port. An accumulator for accumulating oil pressure leaking from the pressure leak port; and the pressure leak from the accumulator side A check valve to prevent backflow of the hydraulic oil to over-up side, and the accumulator and the hydraulic circuit can be switched communication and disconnection between the control valve, wherein supplied to the hydraulic circuit through the discharge port If the discharge amount of the hydraulic oil is insufficient, in communication with the accumulator to the hydraulic circuit by the control valve, the hydraulic oil in the accumulator and a control device supplying to said hydraulic circuit, wherein the control device A hydraulic pressure supply device is provided, which communicates the accumulator with the hydraulic circuit when the pressure in the accumulator exceeds a predetermined pressure .

  The pressure leak port may communicate with the pump chamber at least in the process of reducing the volume of the pump chamber.

  The oil pump is driven by a driving force of an engine, and the controller determines that the pressure in the accumulator is determined to exceed the predetermined pressure based on the number of revolutions and operating time of the engine. An accumulator may be in communication with the hydraulic circuit.

  The pressure sensor may be provided to detect the pressure in the accumulator, and the controller may communicate the accumulator with the hydraulic circuit when the pressure detected by the pressure sensor exceeds a predetermined threshold. .

  The hydraulic circuit may be a hydraulic circuit of an automatic transmission of a vehicle.

In order to solve the above problems, according to another aspect of the present invention, there is provided a drive rotor having external teeth, and a driven rotor having internal teeth and meshed with the drive rotor, and a driving force of an engine. The hydraulic fluid is introduced through the suction port by the volume change of the pump chamber formed between the drive rotor and the driven rotor according to the rotation of the drive rotor and the driven rotor according to the rotation of the drive rotor and the driven rotor. In a control method of a hydraulic pressure supply device for supplying hydraulic fluid to the hydraulic circuit by an oil pump that discharges the hydraulic fluid to the hydraulic circuit, whether the discharge amount of the hydraulic fluid supplied to the hydraulic circuit is insufficient determining whether, even when the discharge amount of the hydraulic fluid is insufficient, re via a pressure leak port communicating with the pump chamber When the pressure in the accumulator that accumulates the hydraulic pressure click exceeds a predetermined pressure, after connection and disconnection between the intake port and the pump chamber, in communication before the position between the discharge port and the pump chamber, prior Symbol It communicates the accumulator to the hydraulic circuit, and a step of supplying the hydraulic oil in the accumulator to the hydraulic circuit, the control method of the hydraulic pressure supply device is provided.

  As described above, according to the present invention, it is possible to store pressure in the accumulator while enabling stable supply of hydraulic fluid to the hydraulic circuit regardless of the rotation range of the oil pump.

It is a schematic diagram which shows schematic structure of the hydraulic-pressure supply apparatus concerning embodiment of this invention. It is explanatory drawing which shows the mode of the oil pump at the time of completion | finish of the suction stroke of the pump chamber P. FIG. It is explanatory drawing which shows the mode of the oil pump in precompression stroke of the pump chamber P. As shown in FIG. It is explanatory drawing which shows the mode of the oil pump at the time of the discharge stroke start of pump chamber P. FIG. It is a flowchart which shows an example of the control method of a hydraulic pressure supply apparatus. It is a characteristic view showing the relation between engine number of rotations and pressure of pump room P. It is a timing chart which shows an example of a control method of an oil pressure supply device.

  The present invention will now be described more fully with reference to the accompanying drawings, in which exemplary embodiments of the invention are shown. In the present specification and the drawings, components having substantially the same functional configuration will be assigned the same reference numerals and redundant description will be omitted.

<< 1. Hydraulic supply system >>
<1-1. Overall configuration of hydraulic supply system>
First, an example of the entire configuration of a hydraulic pressure supply device according to an embodiment of the present invention will be described. FIG. 1 is a schematic view showing an example of the entire configuration of the hydraulic pressure supply device 10. As shown in FIG. The hydraulic pressure supply device 10 shows an example of a device for supplying hydraulic oil in the oil strainer 11 to a belt type automatic transmission. The hydraulic pressure supply device 10 includes an oil pump 20, a hydraulic circuit 40 for guiding hydraulic fluid discharged by the oil pump 20 to an automatic transmission, and an accumulator circuit 33.

<1-2. Hydraulic circuit>
In the hydraulic pressure supply device 10 according to the present embodiment, the hydraulic circuit 40 is configured to include the branched clutch system oil passage 40 a and the line pressure system oil passage 40 b. Among these, the clutch system oil passage 40a leads hydraulic oil to the forward clutch FWDCCH and the reverse clutch REVCCH. The clutch system oil passage 40a is provided with a control valve 43 that switches the supply destination of hydraulic fluid to the forward clutch FWDCCH or the reverse clutch REVCCH. Further, the line pressure system oil passage 40b guides the working oil to the primary pulley, the secondary pulley, and the like.

  The hydraulic circuit 40 is not limited to one that guides the hydraulic oil to the clutch oil passage 40a or the line pressure oil passage 40b. That is, the hydraulic pressure supply device 10 is not limited to one that supplies the hydraulic fluid to the automatic transmission.

<1-3. Oil pump>
The oil pump 20 is a trochoid pump, and sucks in the hydraulic oil in the oil strainer 11 and discharges the sucked hydraulic oil to the hydraulic circuit 40. The oil pump 20 includes a drive rotor 23 having external teeth 23a, a driven rotor 21 having internal teeth 21a, and a housing 29 in which the drive rotor 23 and the driven rotor 21 are incorporated.

  The drive rotor 23 is splined to the crankshaft 19 and has external teeth 23a of trochoid tooth shape. The driven rotor 21 is formed in an annular shape, and the inner teeth 21 a provided on the inner periphery mesh with the outer teeth 23 a of the drive rotor 23. The crankshaft 19 is connected to a drive shaft of an engine (not shown). That is, the oil pump 20 is driven by the driving force of the engine.

  The internal teeth 21 a of the driven rotor 21 are provided one more than the number of the external teeth 23 a of the drive rotor 23. When the drive rotor 23 rotates with the rotation of the crankshaft 19, the driven rotor 21 also rotates. At this time, the rotation center of the driven rotor 21 deviates from the rotation center of the drive rotor 23, and the driven rotor 21 is eccentric to the drive rotor 23.

  Between the external teeth 23 a of the drive rotor 23 and the internal teeth 21 a of the driven rotor 21, there are formed a plurality of pump chambers P which move while expanding and reducing the volume as the drive rotor 23 and the driven rotor 21 rotate. Ru. A housing cover (not shown) is attached to the housing 29 on both axial sides of the drive rotor 23 and the driven rotor 21. The pump chamber P is closed by a housing cover. The housing cover is provided with a suction recess 25 and a discharge recess 27 on the surface facing the drive rotor 23 and the driven rotor 21. In FIG. 1, the arrangement positions of the suction recess 25 and the discharge recess 27 are indicated by hatched regions.

  A suction port 15 is provided in the suction recess 25 of the housing cover. The suction pipe 13 of the oil strainer 11 is connected to the suction port 15. The pump chamber P gradually expands in volume as the drive rotor 23 and the driven rotor 21 rotate at a position facing the suction recess 25. During this time, the pump chamber P communicates with the suction port 15, and the hydraulic oil in the oil strainer 11 is sucked into the pump chamber P via the suction pipe 13 and the suction port 15 (suction stroke).

  On the other hand, a discharge port 17 is provided in the discharge recess 27 of the housing cover. A hydraulic circuit 40 is connected to the discharge port 17. The pump chamber P gradually reduces its volume as the drive rotor 23 and the driven rotor 21 rotate at a position facing the discharge recess 27. During this time, the pump chamber P is in communication with the discharge port 17, and the hydraulic oil in the pump chamber P is discharged to the hydraulic circuit 40 via the discharge port 17 (discharge stroke).

  When the pump chamber P moves with the rotation of the drive rotor 23 and the driven rotor 21, the suction recess 25 and the suction recess 25 are between the position where the pump chamber P faces the suction recess 25 and the position where the pump chamber P faces the discharge recess 27. There is a range that does not face any of the discharge recesses 27. In such a range, the pump chamber P is closed by the external teeth 23a of the drive rotor 23, the internal teeth 21a of the driven rotor 21 and the housing cover, and the hydraulic oil in the pump chamber P is confined (closing stroke). By providing the closing stroke, the communication between the suction port 15 and the discharge port 17 is prevented.

  At any point in the closing stroke, the volume of the pump chamber P may be maximum. Therefore, the hydraulic oil in the pump chamber P can be compressed (pre-compression stroke) in a period from when the volume of the pump chamber P is maximized to when the pump chamber P faces the discharge recess 27. That is, at least the second half of the closing stroke is a precompression stroke. Since the hydraulic fluid is compressed in the pre-compression stroke, bubbles in the hydraulic fluid are crushed and the hydraulic pressure in the hydraulic circuit 40 is prevented from becoming unstable.

<1-4. Accumulator circuit>
One end of the pressure accumulation circuit 33 is connected to the pressure leak port 31 provided in the oil pump 20, and the other end is connected to any position of the hydraulic circuit 40. In FIG. 1, the other end of the pressure accumulation circuit 33 is connected to the clutch oil passage 40a, but may be connected to the line pressure oil passage 40b or may be connected to the hydraulic circuit 40 before branching. The pressure accumulation circuit 33 includes a check valve 35, an accumulator 37 and a control valve 39 in order from the pressure leak port 31 side.

  The pressure leak port 31 is formed at a position in communication with the pump chamber P at least while the pump chamber P is in the pre-compression stroke. Therefore, in the pre-compression stroke, part of the hydraulic oil in the pump chamber P may leak to the pressure accumulation circuit 33. The opening area of the pressure leak port 31 is not particularly limited. However, the pressure leak port 31 is not communicated with the suction port 15 or the discharge port 17 via the pump chamber P.

  FIGS. 2 to 4 are diagrams for describing the arrangement position of the pressure leak port 31, and show the state of the oil pump 20 during the closing stroke. FIG. 2 shows the state in which the suction stroke has ended. FIG. 3 shows a state in which the precompression stroke is started and the hydraulic fluid in the pump chamber P may leak. FIG. 4 shows a state in which the precompression stroke is completed and the discharge stroke is started.

  As shown in FIG. 2, the pressure leak port 31 communicates with the pump chamber P after the pump chamber P is released from the position facing the suction recess 25 and the suction stroke in which the hydraulic oil is sucked into the pump chamber P is completed. Thereafter, when the drive rotor 23 and the driven rotor 21 rotate and the volume of the pump chamber P starts to decrease, as shown in FIG. 3, a precompression stroke is started, and a portion of the boosted hydraulic oil is a pressure leak port It is possible to leak from 31. Furthermore, when the drive rotor 23 and the driven rotor 21 rotate, as shown in FIG. 4, the communication between the pump chamber P and the pressure leak port 31 is interrupted. Thereafter, with a slight delay, the pump chamber P is moved to the position facing the discharge recess 27, and the discharge stroke is started.

  The check valve 35 allows hydraulic fluid leaking through the pressure leak port 31 to flow toward the accumulator 37, while blocking backflow of hydraulic fluid from the accumulator 37 side. The check valve 35 can be, for example, a known check valve provided with a valve body and a valve spring that biases the valve body toward the valve seat.

  The accumulator 37 is a pressure accumulator, and accumulates hydraulic oil leaking through the pressure leak port 31. The hydraulic oil leaking through the pressure leak port 31 is pressurized by the pre-compression stroke. Therefore, the accumulator 37 holds and stores the pressure of the boosted hydraulic oil. The accumulator 37 has a configuration capable of applying an external force to the inflowing hydraulic oil. Therefore, when the pressure of the hydraulic oil leaking via the pressure leak port 31 exceeds the sum of the valve opening pressure of the check valve 35 and the pressure in the accumulator 37, the hydraulic oil may flow into the accumulator 37.

  On the other hand, when the pressure is accumulated in the accumulator 37 and the pressure in the accumulator 37 increases, the pressure in the accumulator 37 is maintained without the check valve 35 opening. In this state, the leak of hydraulic oil through the pressure leak port 31 is stopped.

  The control valve 39 is controlled by the control device 100 to switch communication and shutoff between the accumulator 37 and the hydraulic circuit 40. The control valve 39 can be, for example, a solenoid on-off valve that is switched between open and close by energization and non-energization. In the present embodiment, the control valve 39 is a solenoid on-off valve that closes in the non-energized state and opens in the energized state. The control valve 39 is opened when the flow rate of the hydraulic fluid discharged from the oil pump 20 to the hydraulic circuit 40 may be insufficient for the required flow rate. As a result, the hydraulic oil accumulated in the accumulator 37 is supplied to the hydraulic circuit 40, and the flow rate of the hydraulic oil in the hydraulic circuit 40 is secured.

  The control valve 39 is not limited to the above-described solenoid on-off valve as long as the control valve 39 can switch between communication and disconnection between the accumulator 37 and the hydraulic circuit 40. For example, the control valve 39 may be a three-way solenoid valve provided at a connection portion between the pressure accumulation circuit 33 and the hydraulic circuit 40.

  In the pressure accumulation circuit 33, the accumulator 37 does not accumulate hydraulic oil discharged by the oil pump 20, but accumulates pressurized hydraulic oil that leaks from the oil pump 20. Therefore, it is possible to store pressure in the accumulator 37 without reducing the flow rate of the hydraulic fluid which is discharged by the oil pump 20 and supplied to the automatic transmission through the hydraulic circuit 40. As a result, even when the oil pump 20 is driven in a low rotation range where the flow rate balance of hydraulic fluid in the automatic transmission is severe, the hydraulic pressure can be stably supplied to the automatic transmission.

  Further, in the pressure accumulation circuit 33, as long as the oil pump 20 is driven, the hydraulic oil leaking from the pump chamber P in the pre-compression stroke can be accumulated in the accumulator 37. Therefore, at the latest, after starting operation of oil pump 20, accumulation of pressure in accumulator 37 is completed in a relatively short time. Therefore, the pressure accumulation in the accumulator 37 is completed when the drive state of the oil pump 20 reaches a high rotation region where bubbles in the working oil increase. As a result, when the oil pump 20 is driven at a high rotation speed, the function of collapsing air bubbles in the hydraulic oil is also maintained without leakage of the hydraulic oil from the pump chamber P in the pre-compression stroke.

  Furthermore, in the case of the hydraulic pressure supply device 10 provided with the pressure accumulation circuit 33, there is no need to provide a driving means such as an electric pump for pressure accumulation in the accumulator 37, so power consumption is suppressed and production cost is reduced. The increase can also be suppressed.

<< 2. Control method of hydraulic supply system >>
The configuration of the hydraulic pressure supply device 10 according to the present embodiment has been described above. Next, an example of a control method of the hydraulic pressure supply device 10 will be described. As described above, in the hydraulic pressure supply device 10, accumulation of pressure in the accumulator 37 is performed along with driving of the oil pump 20. Here, mainly, hydraulic oil accumulated in the accumulator 37 is supplied to the hydraulic circuit 40. Control will be described. The control described below is executed by, for example, the control device 100 configured by a microcomputer or the like.

<2-1. Flowchart>
FIG. 5 is a flowchart showing an example of a control method of the hydraulic pressure supply device 10. First, in step S10, the control device 100 determines whether or not the accumulated pressure of the accumulator 37 is sufficient. The hydraulic pressure supply device 10 shown in FIG. 1 does not include a pressure sensor that detects the pressure in the accumulator 37. In this case, the control device 100 determines, for example, based on the engine speed and the operating time, whether or not the accumulated pressure of the accumulator 37 is sufficient. Specifically, in the control device 100, the pressure in the accumulator 37 is determined depending on whether or not a predetermined time or more has elapsed since the engine speed Ne has become equal to or higher than the number Ne0 of revolutions necessary for pressure accumulation in the accumulator 37. It can be determined whether the predetermined pressure is exceeded.

Since the oil pump 20 is driven by the driving force of the engine, the control device 100 makes the determination using the engine rotational speed, but instead of the engine rotational speed, the rotational speed of the oil pump 20 may be used . However, by using the engine rotational speed, it is possible to use the sensor value of the conventionally provided rotational speed sensor, and it is not necessary to newly provide a rotational speed sensor for measuring the rotational speed of the oil pump 20. The value Ne0 of the engine rotational speed necessary for accumulating pressure in the accumulator 37 can be, for example, a rotational speed at which the pressure P _P of the hydraulic fluid in the pump chamber P can be the maximum value P_thre.

Figure 6 shows a characteristic diagram showing the relationship between the pressure P _P of the hydraulic oil in the engine rotational speed Ne and the pump chamber P. The pressure P _P in the pump chamber P is in the low engine rotational speed Ne region, increases as the engine rotational speed Ne increases. The pressure P _P of the pump chamber P becomes substantially constant in a region where the engine speed Ne exceeds the predetermined value Ne0. The value Ne0 of the engine rotational speed at which the pressure P _P becomes a substantially constant value P_thre can be obtained in advance. This value Ne0 can be various values depending on the difference between the engine or the oil pump 20, but can be, for example, 1,000 to 1,500 rpm corresponding to the minimum shift rotational speed.

  In addition, a predetermined time after the engine speed Ne becomes a value Ne0 necessary for pressure accumulation in the accumulator 37 may be obtained in advance as a time necessary for the pressure in the accumulator 37 to exceed the predetermined pressure. it can. For example, the predetermined time until the pressure in the accumulator 37 exceeds the predetermined pressure may be 600 to 1,000 milliseconds.

  When it is determined in step S10 that the pressure accumulation of the accumulator 37 is not sufficient (S10: No), the control device 100 repeats the determination of step S10 until it is determined that the pressure accumulation of the accumulator 37 is sufficient. Then, when it is determined that the accumulated pressure of the accumulator 37 is sufficient (S10: Yes), the control device 100 proceeds to step S20. Normally, after the engine is started, driving of the oil pump 20 is started, and after the pressure in the accumulator 37 exceeds a predetermined pressure, step S10 becomes Yes.

  Next, in step S20, the control device 100 determines whether the line pressure can be reduced. For example, in the low rotation region of the engine, the consumption flow rate of the hydraulic oil in the automatic transmission increases, and the discharge flow rate of the hydraulic oil by the oil pump 20 is insufficient, and the line pressure may be reduced. Specifically, when the vehicle is decelerating, a Low return shift is performed to change the gear ratio of the belt-type automatic transmission toward Low, or the position of the select lever of the automatic transmission is changed, etc. , The consumption flow rate of hydraulic oil in the automatic transmission tends to increase.

  Therefore, the control device 100 can reduce the line pressure based on the sensor value Acc of the accelerator position sensor that detects the operation amount of the accelerator pedal, the sensor value Sp of the select position sensor that detects the position of the select lever, and the like. It can be determined whether or not. However, the method of determining whether or not the line pressure may be reduced is not limited to the above example.

  The hydraulic circuit 40 may be provided with a pressure sensor, and the hydraulic oil accumulated in the accumulator 37 may be supplied to the hydraulic circuit 40 when the detected line pressure falls below a predetermined threshold. However, it is possible to start the supply of hydraulic fluid from the accumulator 37 to the hydraulic circuit 40 in advance before the line pressure actually decreases by determining whether the line pressure can be reduced or not. Can be prevented in advance.

  When the line pressure is not in a state where it can be reduced (S20: No), there is no need to supply hydraulic fluid accumulated in the accumulator 37 to the hydraulic circuit 40, so the control device 100 returns to step S10 and repeats the determination process. . On the other hand, when it is determined that the line pressure may decrease (S20: Yes), the control device 100 proceeds to step S30, and supplies the hydraulic oil accumulated in the accumulator 37 to the hydraulic circuit 40.

  Specifically, the control device 100 energizes the control valve 39 to open the control valve. As a result, the accumulator 37 and the hydraulic circuit 40 communicate with each other. When the line pressure is reduced, the pressure in the accumulator 37 exceeds the line pressure, so that hydraulic fluid accumulated in the accumulator 37 is supplied to the hydraulic circuit 40 as the accumulator 37 and the hydraulic circuit 40 communicate with each other. . As a result, the line pressure rises, and the consumption flow rate of the hydraulic oil in the automatic transmission is secured.

  Next, in step S40, the control device 100 determines whether the elapsed time from the start of supplying the hydraulic fluid accumulated in the accumulator 37 to the hydraulic circuit 40 has exceeded a threshold. The threshold value can be set to the time required for all the hydraulic pressure accumulated in the accumulator 37 to be discharged to the hydraulic circuit 40. The threshold may be, for example, 5 seconds, but is not limited to this value.

  The controller 100 repeats the determination in step S40 until the elapsed time reaches the threshold, and when the elapsed time reaches the threshold (S40: yes), the controller 100 proceeds to step S50 to supply the hydraulic oil from the accumulator 37. finish. Thereafter, the control device 100 returns to step S10 and repeats the process according to the procedure described above. As a result, the consumption flow rate of the hydraulic oil in the automatic transmission increases, and the line pressure can be maintained even if the discharge flow rate of the hydraulic oil by the oil pump 20 is insufficient for the required flow rate. The consumption flow rate of oil is guaranteed.

2-2. Time chart>
FIG. 7 is a time chart for explaining the control method of the hydraulic pressure supply device 10 described above. This time chart shows the transition of the engine speed Ne, the line pressure, the open / close state of the control valve (electromagnetic on-off valve) 39, and the pressure in the accumulator 37 when Low return shift is performed in the automatic transmission. .

  At time t0, which is the time of engine start, the control valve 39 is closed. When the engine is started at time t0, the line pressure starts to increase because the oil pump 20 is driven. In addition, pressure accumulation in the accumulator 37 is also started after time t0, and the pressure in the accumulator 37 also increases. During this time, as the engine speed Ne increases, the line pressure and the pressure in the accumulator 37 also increase.

  Next, at time t1, the engine speed Ne rises to a predetermined value, and after time t1, the line pressure is maintained at a substantially constant value. Further, by the time t1, the pressure in the accumulator 37 becomes a predetermined pressure, and the pressure accumulation is completed. After time t1, the pressure in the accumulator 37 is maintained at a substantially constant value.

  At time t2, when the vehicle decelerates and the engine rotation speed Ne starts to decrease, the automatic transmission performs Low return shift. From this time t2, the consumption flow rate of hydraulic fluid in the automatic transmission increases and the line pressure starts to decrease, but at t2, the control valve 39 is opened and the hydraulic fluid accumulated in the accumulator 37 is the hydraulic circuit Start to be supplied to 40. Thus, the pressure in the accumulator 37 starts to decrease, and at time t3, all the hydraulic pressure accumulated in the accumulator 37 is discharged to the hydraulic circuit 40. As a result, the line pressure starts to rise again.

  At time t3 when the hydraulic pressure accumulated in the accumulator 37 is discharged to the hydraulic circuit 40, the control valve 39 closes again. Along with this, pressure accumulation in the accumulator 37 is performed again by the hydraulic oil leaking from the oil pump 20, and at time t4, the pressure in the accumulator 37 becomes a predetermined pressure, and pressure accumulation is completed. Also, after the Low return shift is completed, the line pressure is maintained at a predetermined line pressure by the hydraulic oil discharged by the oil pump 20 from time t4.

  As described above, according to the control method of the hydraulic pressure supply device 10 according to the present embodiment, the hydraulic oil accumulated in the accumulator 37 is supplied to the hydraulic circuit 40 when the consumption flow rate of the hydraulic oil in the automatic transmission increases. Be done. Therefore, a significant drop in line pressure is suppressed, and stable operation of the automatic transmission is ensured.

<< 3. Summary >>
As described above, the hydraulic pressure supply device 10 according to the present embodiment accumulates, in the accumulator 37, the pressurized hydraulic oil that leaks from the oil pump 20. Therefore, it is possible to store pressure in the accumulator 37 without reducing the flow rate of the hydraulic fluid which is discharged by the oil pump 20 and supplied to the automatic transmission through the hydraulic circuit 40. Thus, regardless of the rotation range of the oil pump 20, the hydraulic pressure can be stably supplied to the automatic transmission.

  Further, as long as the oil pump 20 is driven, the hydraulic pressure supply device 10 according to the present embodiment can accumulate hydraulic oil leaking from the pump chamber P in the pre-compression stroke into the accumulator 37. Therefore, accumulation of pressure in the accumulator 37 is completed in a relatively short time after the start of driving of the oil pump 20. Therefore, particularly when the oil pump 20 is driven in a high rotation range where air bubbles in the hydraulic oil increase, the hydraulic oil does not leak from the pump chamber P in the pre-compression stroke, and air bubbles in the hydraulic oil are The ability to kill is also maintained.

  Further, since the hydraulic pressure supply device 10 according to the present embodiment does not need to be provided with drive means such as an electric pump for accumulating pressure in the accumulator 37, power consumption is suppressed, and increase in production cost is also suppressed be able to.

  Furthermore, the hydraulic pressure supply device 10 according to the present embodiment executes the control of opening the control valve 39 when the consumption flow rate of the hydraulic oil in the automatic transmission increases, so that the hydraulic oil accumulated in the accumulator 37 Are supplied to the hydraulic circuit 40. As a result, even when the consumption flow rate of the hydraulic oil in the automatic transmission increases, a significant drop in line pressure is suppressed.

  Although the preferred embodiments of the present invention have been described in detail with reference to the accompanying drawings, the present invention is not limited to such examples. It is obvious that those skilled in the art to which the present invention belongs can conceive of various modifications or applications within the scope of the technical idea described in the claims. Of course, it is understood that these also fall within the technical scope of the present invention.

  For example, in the above embodiment, the hydraulic pressure supply device 10 does not include the pressure sensor for detecting the pressure in the accumulator 37, but the pressure sensor may be provided. If such a pressure sensor is provided, in the control method of the hydraulic pressure supply device 10, whether or not the accumulated pressure in the accumulator 37 is sufficient depends on whether or not the pressure detected by the pressure sensor exceeds a predetermined value. It can be determined. Further, if such a pressure sensor is provided, the end timing of the supply of the hydraulic oil from the accumulator 37 to the hydraulic circuit 40 can also be determined depending on whether the sensor value of the pressure sensor falls below a predetermined value.

DESCRIPTION OF SYMBOLS 10 oil pressure supply apparatus 11 oil strainer 13 suction pipe 15 suction port 17 discharge port 19 crankshaft 20 oil pump 21 driven rotor 21a internal tooth 23 drive rotor 23a external tooth 25 suction recess 27 discharge recess 29 housing 31 pressure leak port 33 accumulator circuit 35 Check valve 37 Accumulator 39 Control valve (electromagnetic on-off valve)
40 hydraulic circuit 40a clutch system oil passage 40b line pressure system oil passage 100 control device Acc sensor position of accelerator position sensor Ne engine speed P pump chamber Sp sensor position of select sensor

Claims (6)

A drive rotor having external teeth, and a driven rotor having internal teeth and meshed with the drive rotor, driven by a driving force of an engine, and the drive rotor and the drive rotor along with the rotation of the driven rotor and the driven rotor An oil pump that introduces hydraulic fluid through a suction port and discharges the hydraulic fluid to a hydraulic circuit through a discharge port by a change in volume of a pump chamber formed between the driven rotor and the oil pump;
A pressure leak port communicating with the pump chamber at a position before communication between the pump chamber and the discharge port after disconnection between the pump chamber and the suction port;
An accumulator for accumulating hydraulic pressure leaking from the pressure leak port;
A check valve for preventing the backflow of the hydraulic fluid from the accumulator side to the pressure leak port side;
A control valve capable of switching between communication and disconnection between the accumulator and the hydraulic circuit;
When the discharge amount of the hydraulic oil supplied to the hydraulic circuit through the discharge port is insufficient, the control valve communicates the accumulator with the hydraulic circuit to hydraulic oil in the accumulator through the hydraulic circuit. And a controller for supplying
The control device communicates the accumulator with the hydraulic circuit when the pressure in the accumulator exceeds a predetermined pressure .   The hydraulic pressure supply device according to claim 1, wherein the pressure leak port communicates with the pump chamber at least in a process of reducing the volume of the pump chamber. Prior Symbol controller, when the pressure in the accumulator based on the rotational speed and operating time of the engine is determined to exceed the predetermined pressure, communicates the accumulator to the hydraulic circuit, according to claim 1 Or 2 hydraulic pressure supply apparatus. A pressure sensor for detecting the pressure in the accumulator;
The hydraulic pressure supply device according to claim 1 or 2 , wherein the controller communicates the accumulator with the hydraulic circuit when the pressure detected by the pressure sensor exceeds a predetermined threshold. The hydraulic pressure supply device according to any one of claims 1 to 4 , wherein the hydraulic circuit is a hydraulic circuit of an automatic transmission of a vehicle. A drive rotor having external teeth, and a driven rotor having internal teeth and meshed with the drive rotor, driven by a driving force of an engine, and the drive rotor and the drive rotor along with the rotation of the driven rotor and the driven rotor Actuation to the hydraulic circuit by an oil pump that introduces the hydraulic fluid through the suction port and discharges the hydraulic fluid to the hydraulic circuit through the discharge port due to a change in volume of the pump chamber formed between the driven rotor and the driven rotor In a control method of a hydraulic supply system for supplying oil,
Determining whether the discharge amount of the hydraulic oil supplied to the hydraulic circuit is insufficient;
When the discharge amount of the hydraulic fluid is insufficient and the pressure in the accumulator storing the hydraulic pressure leaking through the pressure leak port communicating with the pump chamber exceeds the predetermined pressure, after connection cutoff of the intake port, in communication before the position between the discharge port and the pump chamber, and a pre-Kia accumulator communicating with the hydraulic circuit supplies the hydraulic oil in the accumulator to the hydraulic circuit Step and
A control method of a hydraulic pressure supply device, comprising:

Images