JP2011069258A - Pump device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To more appropriately deal with aging by driving and controlling an electromagnetic part by changing a duty ratio as a controlled variable by a predetermined ratio whenever it is determined that fluid pressure is short to an appropriate pressure. <P>SOLUTION: When an engine is automatically stopped and working fluid is supplied to a start clutch by an electromagnetic pump instead of a mechanical oil pump, a rotation speed change quantity ΔNtb of turbine rotation speed Ntb in previous automatic start of the engine is calculated (S210, S220). If the rotation speed change quantity ΔNtb is not less than threshold TH (S230), it is determined that blow-up of a turbine occurs and oil pressure applied on the clutch is short to appropriate pressure, and effective duty ratio Ds is renewed to approach toward peak duty ratio Dpeak from initial duty ratio D0, predetermined ratio Dset by predetermined ratio Dset (S250). Appropriate pressure is applied to the clutch by driving the electromagnetic pump by applying current at the effective duty ratio Ds even if aging deterioration occurs on the electromagnetic pump and the clutch. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a pump device that pumps a working fluid to a fluid pressure driven device.

  Conventionally, this type of pump device is mounted on an automatic transmission that outputs the power from the engine to the vehicle axle via the friction engagement device, and is driven by the engine power to supply hydraulic pressure to the friction engagement device. And a hydraulic pump connected to the friction engagement device via a check valve and supplying an oil pressure to the friction engagement device by repeating excitation and non-excitation of the electromagnetic coil has been proposed ( For example, see Patent Document 1).

JP 2008-180303 A

  In the above-described pump device, the performance of the electromagnetic pump may be reduced or the hydraulic pressure required for the friction engagement device may be increased due to aging. In this case, as a result of not being able to supply sufficient hydraulic pressure to the friction engagement device, the friction engagement device slips and smooth power transmission cannot be performed.

  The main purpose of the pump device of the present invention is to appropriately cope with aging.

  The pump device of the present invention employs the following means in order to achieve the main object described above.

The first pump device of the present invention comprises:
A pump device for pumping a working fluid to a fluid pressure driven device,
An electromagnetic pump having a piston that sucks and discharges the working fluid in association with the reciprocating motion, and an electromagnetic unit that reciprocates the piston by electromagnetic force;
A fluid pressure detection estimator for detecting or estimating a fluid pressure acting on the device;
Using a duty ratio that is different from a peak duty ratio, which is a duty ratio when the discharge pressure exhibits a peak, in a duty ratio range that can be used as a duty ratio of the current applied to the electromagnetic unit as a default value of the control amount Drive that drives and controls the electromagnetic unit by changing the control amount from the default value to approach the peak duty ratio when the detected or estimated fluid pressure is insufficient with respect to the appropriate pressure. A control unit;
It is a summary to provide.

  In the first pump device of the present invention, a duty ratio different from a peak duty ratio that is a duty ratio when the discharge pressure shows a peak in a duty ratio range that can be used as a duty ratio of a current applied to the electromagnetic unit. Is used as the default value of the control amount, and the electromagnetic part is driven and controlled.When the fluid pressure acting on the fluid pressure drive device is insufficient relative to the appropriate pressure, the control amount is set so that the duty ratio approaches the peak duty ratio from the default value. Change and drive control of the electromagnetic part. Thereby, the fluid pressure supplied to the fluid pressure driven device can be set to an appropriate pressure regardless of the secular change.

  In such a first pump device of the present invention, the drive control unit changes the duty ratio as the control amount by a predetermined ratio every time it is determined that the detected or estimated fluid pressure is insufficient with respect to the appropriate pressure. Thus, the electromagnetic unit can be driven and controlled.

The second pump device of the present invention is
A pump device for pumping a working fluid to a fluid pressure driven device,
An electromagnetic pump having a piston that sucks and discharges the working fluid in association with the reciprocating motion, and an electromagnetic unit that reciprocates the piston by electromagnetic force;
A fluid pressure detection estimator for detecting or estimating a fluid pressure acting on the device;
Drive control of the electromagnetic unit using a frequency that is different from the peak frequency, which is a frequency when the discharge pressure has a peak, in the frequency range that can be used as the frequency of the current applied to the electromagnetic unit as a default value of the control amount A drive control unit that drives and controls the electromagnetic unit by changing a control amount so as to approach the peak frequency from the default value when the detected or estimated fluid pressure is insufficient with respect to an appropriate pressure;
It is a summary to provide.

  In the second pump device of the present invention, the control amount defaults to a frequency different from the peak frequency, which is the frequency when the discharge pressure shows a peak, in the frequency range that can be used as the frequency of the current applied to the electromagnetic unit. When the fluid pressure acting on the fluid pressure drive device is insufficient relative to the appropriate pressure, the control amount is changed so that the frequency approaches the peak frequency from the default value. Drive control. Thereby, the fluid pressure supplied to the fluid pressure driven device can be set to an appropriate pressure regardless of the secular change.

  In such a second pump device of the present invention, the drive control unit changes the frequency as the control amount by a predetermined value every time it is determined that the detected or estimated fluid pressure is insufficient with respect to the appropriate pressure. The electromagnetic unit can be driven and controlled.

  In addition, an input shaft is connected to the output shaft of the prime mover capable of intermittent operation, and is mounted on a power transmission device that transmits power input to the input shaft to the output shaft through a friction engagement element. In the first or second pump device of the present invention that pumps the working fluid to the fluid pressure servo of the friction engagement element as a device, the fluid is actuated by the power from the prime mover to the fluid pressure servo of the friction engagement element. A mechanical pump for supplying pressure, and the drive control unit is configured so that fluid pressure acts on a fluid pressure servo of the friction engagement element instead of the mechanical pump while the prime mover is stopped. It is also possible to drive and control the electromagnetic part. In this aspect of the first or second pump device of the present invention, the fluid pressure detection estimator detects a blow-up of the input shaft when the friction engagement element is engaged when the prime mover is started. By estimating the fluid pressure acting on the fluid pressure servo of the friction engagement element, the drive control unit, when the fluid pressure detection estimator detects the rising of the input shaft, The control amount can be changed when the prime mover stops, and the fluid pressure detection estimator detects vibration when the friction engagement element is engaged with the start of the prime mover. The fluid pressure acting on the fluid pressure servo of the friction engagement element is estimated by the control unit, and when the fluid pressure detection estimator detects a vibration of a predetermined level or more, the drive controller When stopped It is also possible to change the control amount. In this way, there is no need to provide a dedicated sensor for detecting the fluid pressure acting on the device.

  Furthermore, in the first or second pump device of the present invention, the drive control unit determines that the detected or estimated fluid pressure is insufficient with respect to an appropriate pressure in a state where the control amount reaches a peak value. In this case, the intermittent operation of the prime mover can be stopped. By so doing, it is possible to suppress the occurrence of defects in the friction engagement elements.

It is a block diagram which shows the outline of a structure of the vehicle 10 carrying the power transmission device 20 as one Example of this invention. It is explanatory drawing which shows the action | operation table | surface of an automatic transmission mechanism. It is an alignment chart which shows the relationship of the rotational speed of each rotation element of an automatic transmission mechanism. 2 is a configuration diagram showing an outline of a configuration of a hydraulic circuit 30. FIG. It is explanatory drawing which shows an example of the relationship between the frequency of an electromagnetic pump, and discharge pressure. It is explanatory drawing which shows an example of the relationship between the duty ratio Ds of an electromagnetic pump, and discharge pressure. 3 is a flowchart showing an example of an automatic stop control routine executed by an ATECU 29; It is a flowchart which shows an example of a learning process.

  Next, embodiments of the present invention will be described using examples.

  FIG. 1 is a configuration diagram showing an outline of a configuration of a vehicle 10 equipped with a power transmission device 20 as an embodiment of the present invention, and FIG. 2 is an operation table of an automatic transmission mechanism 28.

  As shown in the figure, the power transmission device 20 according to the embodiment is configured to be mounted on, for example, an FF (front engine front drive) type vehicle 10. A torque converter 26 with a lock-up clutch that transmits power with torque amplification, an automatic transmission mechanism 28 that transmits power from the torque converter 26 to the wheels 18a and 18b with speed change, and an ATECU 29 that controls the entire apparatus. With. The vehicle 10 of the embodiment includes a main ECU 90 that controls the entire vehicle including the engine 12 and the power transmission device 20, and communicates with the EGECU 16 and the ATECU 29 to control signals and the operation of the engine 12 and the power transmission device 20. Exchanging data about status. The main ECU 90 includes a shift position SP from the shift position sensor 92 that detects the operation position of the shift lever 91, an accelerator opening Acc from the accelerator pedal position sensor 94 that detects the depression amount of the accelerator pedal 93, and the brake pedal 95. The brake switch signal BSW from the brake switch 96 that detects the depression, the vehicle speed V from the vehicle speed sensor 98, and the like are input.

  The torque converter 26 includes a pump impeller 26a connected to the crankshaft 14 of the engine 12, and a turbine runner 26b connected to the input shaft 22 of the automatic transmission mechanism 28 and disposed opposite to the pump impeller 26a. The pump impeller 26a The engine torque is converted into a flow of hydraulic oil, and the flow of the hydraulic oil is converted into torque on the input shaft 22 by the turbine runner 26b to transmit torque. The torque converter 26 has a built-in lock-up clutch 26c. When the lock-up clutch 26c is engaged, the engine crankshaft 14 and the input shaft 22 of the automatic transmission mechanism 28 are directly connected to each other to directly engine torque. To communicate.

  The automatic transmission mechanism 28 includes a planetary gear unit PU, three clutches C1, C2, and C3, two brakes B1 and B2, and a one-way clutch F1. The planetary gear unit PU is configured as a Ravigneaux type planetary gear mechanism, and includes two sun gears S1 and S2 as external gears, a ring gear R as an internal gear, a plurality of short pinion gears PS meshing with the sun gear S1, and a sun gear. S2 and a plurality of long pinion gears PL that mesh with the plurality of short pinion gears PS and mesh with the ring gear R, and a carrier CR that holds the plurality of short pinion gears PS and the plurality of long pinion gears PL in a freely rotating and revolving manner. The sun gear S1 is connected to the input shaft 22 via the clutch C1, and the sun gear S2 is connected to the input shaft 22 via the clutch C3, and its rotation is freely or prohibited by the brake B1. The ring gear R is connected to the output shaft 24. Cage, carrier CR is connected to the input shaft 22 via the clutch C2. Further, the rotation of the carrier CR is restricted in one direction by the one-way clutch F1, and the rotation of the carrier CR is freely or prohibited by a brake B2 provided in parallel to the one-way clutch F1. The power output to the output shaft 24 is transmitted to the wheels 18a and 18b via a counter gear and a differential gear (not shown).

  Further, as shown in the operation table of FIG. 2, the automatic transmission mechanism 28 can switch between forward 1st speed to 4th speed and reverse speed by a combination of on / off of the clutches C1 to C3 and the brakes B1 and B2. Yes. FIG. 3 is a collinear diagram showing the relationship among the rotational speeds of the sun gears S1, S2, the ring gear R, and the carrier CR at each gear stage of the automatic transmission mechanism 28.

  The hydraulic circuit 30 turns on and off the clutches C1 to C3 and on and off the brakes B1 and B2 in the automatic transmission mechanism 28. FIG. 4 is a configuration diagram showing an outline of the configuration of the hydraulic circuit 30. As shown in the figure, the hydraulic circuit 30 includes a mechanical oil pump 32 that pumps hydraulic oil through the strainer 31 by power from the engine, and a line pressure PL that regulates the hydraulic oil pumped from the mechanical oil pump 32. A regulator valve 33 for generating a pressure, a linear solenoid SLT for driving the regulator valve 33 by adjusting a modulator pressure PMOD generated from a line pressure PL via a modulator valve (not shown) and outputting it as a signal pressure, and a line pressure PL Input port 42a, drive position output port (D port) 42b, reverse position output port (R port) 42c, etc. are formed, and input port 42a and output ports 42b, 42c are interlocked with the operation of shift lever 91. Manual for communication and disconnection between Via the lube 40, the normally closed linear solenoid SLC 1 that inputs the hydraulic oil output from the D port 42 b of the manual valve 40 from the input port 52 a and adjusts and outputs the pressure from the output port 52 b, and the mechanical oil pump 32. The electromagnetic pump 70 having the suction port 72a connected to the strainer 31 and the discharge port 72b connected to the clutch C1 (clutch oil passage 38) via the discharge port oil passage 35, and the output port of the linear solenoid SLC1. 52 b (output port oil passage 34) and forward first speed (starting) clutch C 1 (clutch oil passage 38) are connected to and disconnected from the switching valve 60, and are connected to the clutch oil passage 38. The accumulator 39 is used. In FIG. 4, the hydraulic systems of the clutches C2 and C3 other than the clutch C1 and the brakes B1 and B2 are omitted because they do not form the core of the present invention. Can be configured.

  The electromagnetic pump 70 incorporates a suction check valve 74 and a discharge check valve 76 in a piston 73 that slides in a sleeve 72. When the solenoid unit 71 is turned off, the discharge check valve 76 is discharged. Is closed and the suction check valve 74 is opened to suck hydraulic oil from the suction port 72a. When the solenoid 71 is turned on from off, the suction check valve 74 is closed and the discharge check is stopped. The valve 76 opens to discharge the hydraulic fluid sucked from the discharge port 72b. FIG. 5 shows the relationship between the frequency of the current applied to the electromagnetic pump 70 and the discharge pressure, and FIG. 6 shows the duty ratio Ds when driving the electromagnetic pump 70 with the current of the frequency H0 when the discharge pressure shows a peak. The relationship with discharge pressure is shown. The electromagnetic pump 70 is designed to have a pumping capacity higher than the discharge pressure P0 required for applying an appropriate pressure to the clutch C1, and in the embodiment, the initial duty is obtained so that the discharge pressure P0 is obtained at the time of product shipment. It is driven using the range from the ratio D0 to the peak duty ratio Dpeak in which the maximum discharge pressure P1 is obtained.

  The switching valve 60 includes a signal pressure input port 62a for inputting the line pressure PL as a signal pressure, an input port 62b connected to the output port 52b (output port oil passage 34) of the linear solenoid SLC1, and a clutch C1 (clutch oil passage). 38), a sleeve 62 in which various ports of the output port 62c are formed, a spool 64 that slides in the sleeve 62 in the axial direction, and a spring 66 that biases the spool 64 in the axial direction. Yes. When the line pressure PL is input to the signal pressure input port 62a, the switching valve 60 overcomes the urging force of the spring 66 and the spool 64 moves to the position shown in the left half region in the figure, and the input port 62b and the output port 62c communicates with the output port oil passage 34 and the clutch oil passage 38, and when the line pressure PL is not input to the signal pressure input port 62a, the spool 64 is urged by the urging force of the spring 66 in the drawing. The communication between the input port 62b and the output port 62c is cut off by moving to the position shown in the right half region, thereby blocking the communication between the output port oil passage 34 and the clutch oil passage 38.

  Although not shown, the ATECU 29 is configured as a microprocessor centered on a CPU. In addition to the CPU, a ROM that stores a processing program, a RAM that temporarily stores data, an input / output port, and a communication port Is provided. The AT ECU 29 receives the turbine rotation speed Ntb and the like from a rotation speed sensor 99 attached to the input shaft 22 via an input port.

  In the vehicle 10 of the embodiment configured in this way, when the shift lever 91 is running at the D (drive) running position, the vehicle speed V is set to 0, the accelerator is turned off, the brake switch signal BSW is turned on, and so on. The engine 12 is automatically stopped when all of the automatic stop conditions are satisfied. When the engine 12 is automatically stopped, thereafter, the engine 12 that has been automatically stopped is automatically started when a preset automatic start condition such as the brake switch signal BSW being turned off is satisfied.

  Next, the operation of the vehicle 10 of the embodiment configured as described above, particularly, the operation when the engine 12 that is automatically stopped is automatically started will be described. FIG. 7 is a flowchart showing an example of an automatic stop control routine executed by the ATECU 29. This routine is executed when the aforementioned automatic stop condition is satisfied.

  When the automatic stop control routine is executed, the ATECU 29 maximizes the current applied to the linear solenoid SLC1 when the engine 12 is stopped (step S100) (step S110), and the peak frequency H0 and the execution duty. The driving of the electromagnetic pump 70 is started with the ratio Ds (step S120), and then it is waited for the automatic start condition of the engine 12 to be satisfied (step S130). Here, the execution duty ratio Ds is a duty ratio of the current applied to the coil of the solenoid unit 71, and is set by a learning process described later. When the automatic stop condition is satisfied and the engine 12 is automatically stopped, the mechanical oil pump 32 is also stopped accordingly, so that the line pressure PL is released, and the spool 64 of the switching valve 60 is connected to the output port oil passage 34 and the clutch. The connection with the oil passage 38 is cut off. Therefore, by driving the electromagnetic pump 70 in which the discharge port 72b is connected to the clutch oil passage 38, hydraulic pressure can be applied to the clutch C1.

  When the automatic start condition of the engine 12 is satisfied, an engine start command is transmitted to the EGECU 16 via the main ECU 90 so that the engine 12 is automatically started (step S140), and executed by executing a learning process illustrated in FIG. The duty ratio Ds is set (step S150), and when the engine 12 is completely detonated (step S160), the driving of the electromagnetic pump 70 is stopped (step S170), and this routine is terminated. When the engine 12 is automatically started, the mechanical oil pump 32 is activated, and the hydraulic oil pressure-fed from the mechanical oil pump 32 is supplied to the clutch C1 via the linear solenoid SLC1. As described above, since the hydraulic oil is supplied from the electromagnetic pump 70 to the clutch C1 when the engine 12 is automatically stopped, the clutch C1 can be quickly engaged immediately after the engine 12 is automatically started. The start can be performed smoothly.

  Next, the learning process of FIG. 6 will be described. In the learning process, it is determined whether or not the current execution duty ratio Ds has been updated (step S200). When it has been updated, the process is terminated. When it has not been updated, the turbine speed Ntb is input from the rotation speed sensor 99 (step S210). The turbine speed Ntb that has been input and the turbine speed that was previously input in this routine (the previous time) Ntb) is used to calculate the rotation change amount ΔNtb (step S220), and the calculated rotation change amount ΔNtb is compared with the threshold value TH (step S230). Here, the threshold value TH is a threshold value for determining whether the input shaft 22 is blown up, and a value obtained in advance by experiments can be used. Considering the case where the engine 12 is automatically started while the vehicle 10 is stopped, the power from the engine 12 is transmitted via the torque converter 26 along with the automatic start when the clutch C1 does not slip. However, the input shaft 22 does not rotate, but when the clutch C1 slips, the input shaft 22 is rotated by the power transmitted from the engine 12 via the torque converter 26 and blown up. In the embodiment, it is determined whether or not the clutch C1 has slipped by detecting the rising of the input shaft 22, and the hydraulic pressure to be applied to the clutch C1 is insufficient due to the aging of the clutch C1 or the electromagnetic pump 70. It is judged whether it has occurred. When the rotation change amount ΔNtb is less than the threshold value TH, it is determined that an appropriate pressure is supplied to the clutch C1, and this process is terminated. When the rotation change amount ΔNtb is equal to or greater than the threshold value TH, the current execution duty ratio Ds is It is determined whether or not it is smaller than the peak duty ratio Dpeak (step S240). When the current duty ratio Ds is smaller than the peak duty ratio Dpeak, a new ratio is added by adding the predetermined ratio Dset to the current duty ratio Dsek. The execution duty ratio Ds is updated (step S250), and this process is terminated. Here, the predetermined ratio Dset is when the execution duty ratio Ds is gradually stepped from the initial duty ratio D0 to the peak duty ratio Dpeak when the hydraulic pressure acting on the clutch C1 is insufficient with respect to the appropriate pressure. , And can be determined as 3% or 5%, for example. When it is determined in step S230 that the rotation change amount ΔNtb is less than the threshold value TH, the appropriate pressure is supplied to the clutch C1, and this process is terminated. The updated execution duty ratio Ds is used when the engine 12 is automatically stopped next time when the automatic stop condition is satisfied. If it is determined in step S240 that the current duty ratio Ds is greater than or equal to the peak duty ratio Dpeak, the clutch C1 has slipped despite the fact that the pumping capacity cannot be increased any more. Even if the stop condition is satisfied, the engine 12 is not automatically stopped (stop of intermittent operation) (step S260). In this case, a warning can be issued to the driver by turning on a warning lamp (not shown).

  According to the power transmission device 20 of the embodiment described above, when the engine 12 automatically stops and the hydraulic oil is supplied to the starting clutch C1 by the electromagnetic pump 70 instead of the mechanical oil pump 32, the clutch C1 It is determined whether or not an appropriate pressure is applied to the engine. When the hydraulic pressure acting on the clutch C1 is insufficient with respect to the appropriate pressure, the execution duty ratio Ds is changed from the initial duty ratio D0 to the peak duty ratio Dpeak. The electromagnetic pump 70 is driven by applying current at the execution duty ratio Ds so that the electromagnetic pump 70 and the clutch C1 are deteriorated over time. Can act. In addition, when the engine 12 is automatically started, it acts on the clutch C1 depending on whether or not the input shaft 22 of the automatic transmission mechanism 28 connected to the crankshaft 14 of the engine 12 via the torque converter 26 is blown up. Since the hydraulic pressure is estimated, there is no need to provide a dedicated sensor. Further, when the current execution duty ratio Ds is already equal to or greater than the peak duty ratio Dpeak when the clutch C1 is slipping, the engine 12 is not automatically stopped even if the automatic stop condition is satisfied next time. Occurrence of problems due to wear of the clutch C1 can be suppressed.

  In the power transmission device 20 of the embodiment, when the hydraulic pressure acting on the clutch C1 is insufficient with respect to the appropriate pressure, the execution duty ratio Ds is made closer to the peak duty ratio Dpeak by the predetermined ratio Dset. The predetermined ratio Dset may be changed based on the degree (in the embodiment, the magnitude of the rotation change amount ΔNtb).

  In the power transmission device 20 of the embodiment, the frequency (cycle) of the current applied to the electromagnetic pump 70 is fixed and only the duty ratio Ds is changed. However, the duty ratio Ds is fixed and only the frequency is changed. It is also possible to change both the frequency and the duty ratio. When changing the frequency of the current applied to the electromagnetic pump 70, the default value is set to a point shifted from the peak frequency H0 when the discharge pressure shows a peak, as shown in FIG. When the hydraulic pressure acting on the pressure is insufficient with respect to the appropriate pressure, the default value may be approached by a predetermined value toward the peak frequency H0. In this case, the predetermined value may be changed according to the degree to which the hydraulic pressure acting on the clutch C1 is insufficient with respect to the appropriate pressure.

  In the power transmission device 20 of the embodiment, the hydraulic pressure acting on the clutch C1 is adjusted to an appropriate pressure by comparing the rotation change amount ΔNtb of the input shaft 22 of the automatic transmission mechanism 28 when the engine 12 is automatically started with a threshold value TH. However, the present invention is not limited to this, and depends on whether the degree of vibration detected by the G sensor when the engine 12 is automatically started is greater than or equal to a threshold value. It may be determined. Alternatively, a hydraulic pressure sensor may be provided in the clutch oil passage 38 and the determination may be made based on the hydraulic pressure detected by the hydraulic pressure sensor.

  In the power transmission device 20 of the embodiment, the intermittent operation of the engine 12 is stopped when the execution duty hDs is equal to or greater than the peak duty ratio Dpeak, but the intermittent operation may be performed.

  In the power transmission device 20 of the embodiment, the automatic transmission mechanism 28 of the forward first speed to the fourth speed four-speed transmission is provided. However, the automatic transmission mechanism is not limited to this, and the two-speed transmission or the like. Any number of stages such as a three-stage shift or five or more stages may be used.

  Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. In the embodiment, the clutch C1 corresponds to “fluid pressure driven device”, the electromagnetic pump 70 corresponds to “electromagnetic pump”, the rotational speed sensor 99, and the AT ECU 29 that executes steps S210 to S230 of the learning process of FIG. Corresponds to the “fluid pressure detection estimator”, and the ATECU 29 that executes the control routine at the time of automatic stop in FIG. 7 and the learning process in FIG. 8 corresponds to the “drive control unit”. The mechanical oil pump 32 corresponds to a “mechanical pump”. The correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is the same as that of the embodiment described in the column of means for solving the problem. It is an example for specifically explaining the best mode for doing so, and does not limit the elements of the invention described in the column of means for solving the problem. That is, the interpretation of the invention described in the column of means for solving the problems should be made based on the description of the column, and the examples are those of the invention described in the column of means for solving the problems. It is only a specific example.

  As mentioned above, although embodiment of this invention was described using the Example, this invention is not limited to such an example at all, and can be implemented with a various form within the range which does not deviate from the summary of invention. Of course.

  The present invention is applicable to the power transmission device manufacturing industry.

  DESCRIPTION OF SYMBOLS 10 Vehicle, 12 Engine, 14 Crankshaft, 16 EGECU, 20 Power transmission device, 22 Input shaft, 24 Output shaft, 26 Torque converter, 26a Pump impeller, 26b Turbine runner, 26c Lock-up clutch, 28 Automatic transmission mechanism, 29 AT ECU , 30 Hydraulic circuit, 31 Strainer, 32 Mechanical oil pump, 33 Regulator valve, 34 Output port pressure oil passage, 35 Discharge port oil passage, 38 Clutch oil passage, 39 Accumulator, 40 Manual valve, 42a Input port, 42b D position output port, 42c R position output port, 60 switching valve, 62 sleeve, 62a Signal pressure input port, 62b input port, 62c output port, 64 spool, 66 spring, 7 0 Electromagnetic pump, 71 Solenoid part, 72 Cylinder, 72a Suction port, 72b Discharge port, 73 Piston, 74 Suction check valve, 76 Discharge check valve, 90 Main ECU, 91 Shift lever, 92 Shift position sensor, 93 Accelerator pedal, 94 Accelerator pedal position sensor, 95 Brake pedal, 96 Brake switch, 98 Vehicle speed sensor, 99 Rotational speed sensor, SLT, SLC1 Linear solenoid, S1, S2 Sun gear, R ring gear, PS Short pinion gear, PL Long pinion gear, CR carrier , C1-C3 clutch, B1, B2 brake, F1 one-way clutch.

Claims (8)

A pump device for pumping a working fluid to a fluid pressure driven device,
An electromagnetic pump having a piston that sucks and discharges the working fluid in association with the reciprocating motion, and an electromagnetic unit that reciprocates the piston by electromagnetic force;
A fluid pressure detection estimator for detecting or estimating a fluid pressure acting on the device;
Using a duty ratio that is different from a peak duty ratio, which is a duty ratio when the discharge pressure exhibits a peak, in a duty ratio range that can be used as a duty ratio of the current applied to the electromagnetic unit as a default value of the control amount Drive that drives and controls the electromagnetic unit by changing the control amount from the default value to approach the peak duty ratio when the detected or estimated fluid pressure is insufficient with respect to the appropriate pressure. A control unit;
A pump device comprising: The pump device according to claim 1,
The drive control unit drives and controls the electromagnetic unit by changing a duty ratio as the control amount by a predetermined ratio every time it is determined that the detected or estimated fluid pressure is insufficient with respect to an appropriate pressure. . A pump device for pumping a working fluid to a fluid pressure driven device,
An electromagnetic pump having a piston that sucks and discharges the working fluid in association with the reciprocating motion, and an electromagnetic unit that reciprocates the piston by electromagnetic force;
A fluid pressure detection estimator for detecting or estimating a fluid pressure acting on the device;
Drive control of the electromagnetic unit using a frequency that is different from the peak frequency, which is a frequency when the discharge pressure has a peak, in the frequency range that can be used as the frequency of the current applied to the electromagnetic unit as a default value of the control amount A drive control unit that drives and controls the electromagnetic unit by changing a control amount so as to approach the peak frequency from the default value when the detected or estimated fluid pressure is insufficient with respect to an appropriate pressure;
A pump device comprising: The pump device according to claim 3,
The drive control unit drives and controls the electromagnetic unit by changing the frequency as the control amount by a predetermined value every time it is determined that the detected or estimated fluid pressure is insufficient with respect to an appropriate pressure. An input shaft is connected to an output shaft of a prime mover capable of intermittent operation, and is mounted on a power transmission device that transmits power input to the input shaft to the output shaft via a friction engagement element, as the fluid pressure driven device The pump device according to claim 1, wherein the working fluid is pumped to a fluid pressure servo of the friction engagement element.
A mechanical pump that operates by power from the prime mover and supplies fluid pressure to a fluid pressure servo of the friction engagement element;
The drive control unit drives and controls the electromagnetic unit so that a fluid pressure acts on a fluid pressure servo of the friction engagement element instead of the mechanical pump while the prime mover is stopped. The pump device according to claim 5,
The fluid pressure detection estimator acts on a fluid pressure servo of the friction engagement element by detecting a blow-up of the input shaft when the friction engagement element is engaged with starting of the prime mover. Estimated fluid pressure,
When the fluid pressure detection estimator detects that the input shaft is blown up, the drive control unit changes the control amount when the prime mover stops after the next time. The pump device according to claim 5,
The fluid pressure detection estimator estimates a fluid pressure acting on a fluid pressure servo of the friction engagement element by detecting a vibration when the friction engagement element is engaged with starting of the prime mover. And
The drive control unit changes the control amount when the prime mover stops after the next time when the fluid pressure detection estimator detects a vibration of a predetermined level or more. The pump device according to any one of claims 5 to 7,
The drive control unit stops the intermittent operation of the prime mover when it is determined that the detected or estimated fluid pressure is insufficient with respect to an appropriate pressure in a state where the control amount reaches a peak value. Pump device.

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