JP2008063947A - Oil supplying device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oil supplying device for a vehicle capable of improving the operating efficiency of an electric oil pump without complicating the structure and control of the pump, thereby reducing the power consumption and manufacturing cost. <P>SOLUTION: Oil discharged from a high-pressure pump mechanism part 50 is supplied to a rotating operation mechanism 11 through a line pressure passage 33 and oil discharged from a low-pressure pump mechanism part 51 is supplied to a lubricating/cooling passage 34. The pressure of the line pressure passage 33 is regulated by a pressure regulating valve 35 and excessive oil is supplied to the lubricating/cooling passage 34. A total required flow volume is obtained by adding a leak flow volume during non-operation of the rotating operation mechanism 11 and a flow volume required in the lubricating/cooling passage 34. A number of revolutions N1 required for obtaining the flow volume is calculated. A threshold number of revolutions N2 as a limit value that permits the leak flow volume to be compensated is calculated. When N1 is equal to or larger than N2, an electric motor 52 is driven at N1. When N1 is smaller than N2, the electric motor 52 is driven at N2. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a vehicle oil supply device that supplies oil to a high-pressure oil passage and a low-pressure oil passage by an electric oil pump.

  There is known one that supplies oil for operating a hydraulic actuator of a vehicle and supplies oil for cooling and lubrication of various devices with one electric oil pump (see, for example, Patent Document 1).

  This electric oil pump has a high-pressure pump mechanism and a low-pressure pump mechanism that are driven by a common electric motor, and oil discharged from the high-pressure pump mechanism is mainly used for the operation of the hydraulic actuator. The oil discharged from the section is used for cooling and lubrication of various devices.

In a vehicle oil supply apparatus employing this electric oil pump, a high pressure pump mechanism is connected to a line pressure passage through a pressure regulating valve, and a low pressure pump mechanism is connected to a low pressure oil passage such as a cooling passage or a lubrication passage. ing. The pressure regulating valve on the high pressure pump mechanism section regulates oil supplied to the line pressure passage to a set pressure and supplies surplus oil to the low pressure oil passage.
In addition, the electric oil pump obtains the oil flow rate required for the hydraulic actuator and the oil flow rate required for cooling and lubrication of the equipment, and the drive rotational speed required to obtain these required flow rates is high. The electric motor is driven at one rotational speed. As a result, a shortage of supply oil does not always occur in the line pressure passage on the hydraulic actuator side and the low pressure oil passage for cooling and lubrication.
JP 2000-27992 A

  However, in this conventional oil supply device, the electric motor is driven at the higher rotational speed of the drive rotational speeds required to obtain the required flow rates on the high pressure side and the low pressure side, respectively. Although the shortage of supply oil does not occur, the flow rate of surplus oil increases and unnecessary power consumption of the electric motor increases. Specifically, in order to secure supply oil for cooling and lubrication despite the overwhelming amount of time during which the hydraulic actuator is not operated when the vehicle is in operation, oil with a flow rate higher than necessary is required. It will continue to flow to the hydraulic actuator side, and driving power for flowing this oil will be wasted.

  Therefore, the present invention aims to provide an oil supply device for a vehicle that can increase the operation efficiency of the electric oil pump without complicating the structure and control, and reduce both power consumption and manufacturing cost. To do.

  The invention according to claim 1 for solving the above-described problem is a high-pressure pump mechanism (for example, a high pressure in an embodiment described later) driven by a common electric motor (for example, an electric motor 52 in an embodiment described later). An electric oil pump (for example, an electric oil pump 32 in an embodiment described later) having a pump mechanism section 50) and a low pressure pump mechanism section (for example, a low pressure pump mechanism section 51 in an embodiment described later), and the high pressure pump mechanism section A line pressure passage (for example, a line pressure passage 33 in an embodiment described later) for supplying discharged oil to a hydraulic actuator of the vehicle, and oil discharged from the low-pressure pump mechanism section are supplied to a low-pressure oil utilization section of a vehicle device. Discharge from the low pressure oil passage (for example, the lubrication / cooling passage 34 in the embodiment described later) and the high pressure pump mechanism. The pressure regulating valve that regulates the oil supplied to the line pressure passage to a set pressure and supplies surplus oil to the low pressure oil passage (for example, the pressure regulating valve 35 in an embodiment described later), and the hydraulic actuator is inoperative Sometimes, a leak flow rate calculating means for calculating the flow rate of oil leaking from the hydraulic actuator (for example, a leak flow rate calculating means 60 in an embodiment described later), and a low pressure required for calculating the flow rate of oil required in the low pressure oil passage. The total required flow rate of oil is calculated from the calculation results of the flow rate calculation means (for example, the low pressure required flow rate calculation means 61 in the embodiment described later) and the leak flow rate calculation means and the low pressure required flow rate calculation means when the hydraulic actuator is not operated. Total required flow rate calculating means (for example, total required flow rate calculating means 62 in the embodiment described later), The required motor speed calculating means for calculating the required rotational speed of the electric motor for obtaining the total required flow rate (for example, the required motor speed calculating means 63 in the embodiment described later) and the oil discharge flow rate at the high-pressure pump mechanism section are as follows. Threshold motor speed calculation means (for example, threshold motor speed calculation means 64 in an embodiment described later) for calculating a threshold rotation speed of an electric motor that is substantially the same as the leak flow rate of oil from the hydraulic actuator, and the necessary motor speed calculation. And when the required rotational speed of the electric motor for obtaining the total required flow rate is equal to or higher than the threshold rotational speed when the hydraulic actuator is not operated based on the calculation result of the means and the threshold motor speed calculating means, The required rotational speed of the electric motor for driving at the required rotational speed and obtaining the total required flow rate is the threshold rotational speed. When the angle is smaller than 50 degrees, drive control means for driving the electric motor at a set speed equal to or higher than the threshold rotation speed (for example, drive control means 65 in an embodiment described later) is provided.

  Thus, when the hydraulic actuator is not operating, the leak flow rate calculating means calculates the flow rate of oil leaking from the hydraulic actuator, the low pressure required flow rate calculating means calculates the required oil flow rate in the low pressure oil passage, Based on these calculation results, the total required flow rate of the oil is calculated by the total required flow rate calculation means. Thereafter, the required motor speed calculating means calculates the required rotational speed of the electric motor for obtaining the total required flow rate, and the threshold motor speed calculating means calculates the threshold rotational speed of the electric motor. At this time, if the required rotational speed of the electric motor is equal to or higher than the threshold rotational speed, the electric motor is driven at the required rotational speed by the drive control means, and if the required rotational speed of the electric motor is smaller than the threshold rotational speed, the electric motor Is driven at a set speed equal to or higher than the threshold rotation speed by the drive control means. Therefore, the electric oil pump is basically operated so as to satisfy the total required flow rate of the low pressure side and the high pressure side, and when the flow rate of the oil in the line pressure passage may be lower than the leak flow rate from the hydraulic actuator, it is ensured. The engine is operated at a set speed that is equal to or higher than a threshold rotational speed at which an oil flow rate equal to or higher than the leak flow rate is obtained.

According to a second aspect of the present invention, in the vehicle oil supply device according to the first aspect, the pressure regulating valve is configured such that the high pressure pump is driven when the electric motor is driven at the required rotational speed when the hydraulic actuator is not operated. A flow rate obtained by subtracting a leak flow rate of the hydraulic actuator from a flow rate of oil discharged from the mechanical unit is set to be supplied to the low-pressure oil passage.
As a result, while the electric motor is driven at the required rotational speed when the hydraulic actuator is not operated, surplus oil discharged from the high-pressure pump mechanism is supplied to the low-pressure oil passage through the pressure regulating valve, and the low-pressure oil used in the vehicle equipment is used. Effectively used in departments.

  Invention of Claim 3 is the oil supply apparatus of the vehicle of any one of Claim 1 or 2, The oil supplied to the said line pressure path is used for the action | operation of the hydraulic actuator of a drive mechanism, The oil supplied to the low-pressure oil passage is used for at least one of cooling and lubrication of vehicle equipment.

According to a fourth aspect of the present invention, in the vehicle oil supply device according to any one of the first to third aspects, a temperature detecting means for detecting a temperature of oil discharged from the high-pressure pump mechanism (for example, And a leak flow rate calculating unit that calculates a leak flow rate based on a temperature detected by the temperature detection unit.
As a result, the leak flow rate of the oil from the hydraulic actuator that changes according to the temperature is accurately calculated by the leak flow rate calculation means.

A fifth aspect of the present invention is the vehicle oil supply device according to any one of the first to fourth aspects, further comprising a temperature detection means for detecting a temperature of oil discharged from the high-pressure pump mechanism. The required motor speed calculation means and the threshold motor speed calculation means calculate the required rotation speed and the threshold rotation speed of the electric motor based on the temperature detected by the temperature detection means.
As a result, the required rotation speed and threshold rotation speed of the electric motor that change according to the temperature are accurately calculated by the required motor speed calculation means and the threshold motor speed calculation means.

According to a sixth aspect of the present invention, in the vehicle oil supply device according to any one of the first to fifth aspects, the hydraulic actuator has a permanent magnet (e.g., an embodiment described later) along the circumferential direction. And the inner peripheral side rotor (for example, the inner peripheral side rotor 6 in the embodiments described later) and the outer peripheral side of the inner peripheral side rotor so as to be coaxial and relatively rotatable. An outer circumferential rotor (for example, an outer circumferential rotor 5 in an embodiment described later) disposed with a permanent magnet along the circumferential direction, and the inner circumferential rotor and the outer circumference by hydraulic pressure. An electric motor (for example, an electric motor 1 in an embodiment to be described later) provided with phase changing means (for example, a rotation operation mechanism 11 in an embodiment to be described later) that relatively rotates the side rotor to change the relative phase between the two. ) Of said phase change means And wherein the door.
In this case, for example, when the relative phase between the inner and outer rotors of the electric motor is fixed at an arbitrary position, the oil is continuously supplied to the phase changing means so as to compensate for the oil leak. At this time, oil is supplied to the phase changing means from the electric oil pump, but the electric oil pump is operated so that the oil flow rate in the line pressure passage always exceeds the leak flow rate in the phase changing means. The relative phase between the side rotor and the outer rotor is reliably held at a fixed position.

  According to the first aspect of the present invention, basically, the drive speed of the electric motor is controlled so that the total required flow rates on the low pressure side and the high pressure side are obtained, and the oil flow rate in the line pressure passage is controlled by the hydraulic actuator. The electric motor drive speed is controlled to a set speed that is equal to or higher than the threshold rotational speed that ensures that the oil flow rate is greater than the leak flow rate only when there is a possibility that the leak flow rate will be lower. The power loss of the oil pump can be reliably reduced. Therefore, this makes it possible to reduce power consumption and manufacturing cost of the electric motor.

  According to the second aspect of the present invention, the surplus oil discharged from the high-pressure pump mechanism can be effectively used in the low-pressure oil utilization unit of the vehicle equipment, so that the hydraulic actuator reduces the power loss of the electric motor. It is possible to reliably compensate for oil leakage at the tank.

  According to the third aspect of the present invention, the vehicle equipment can be sufficiently cooled and lubricated while maintaining the holding pressure of the drive mechanism by compensating for the oil leak of the hydraulic actuator.

  According to the fourth aspect of the present invention, the leak flow rate of the oil from the hydraulic actuator can be accurately calculated by reflecting the temperature change of the oil, so that the drive control of the electric motor can be performed more accurately. .

  According to the fifth aspect of the present invention, the required rotation speed and the threshold rotation speed of the electric motor can be accurately calculated by reflecting the temperature change of the oil, so that the drive control of the electric motor can be performed more accurately. Can do.

  According to the sixth aspect of the present invention, it is possible to stably maintain the induced voltage constant of the electric motor at the set value while reducing the power consumption in the electric oil pump.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
1 to 5 show an electric motor 1 used as a travel drive source for a hybrid vehicle, an electric vehicle, or the like. The electric motor 1 is an inner rotor type brushless motor in which a rotor unit 3 is disposed on the inner peripheral side of an annular stator 2. The stator 2 has a multi-phase stator winding 2a, and the rotor unit 3 has a rotating shaft 4 at the shaft core. Further, the rotational force of the electric motor 1 is transmitted to a wheel drive shaft (not shown) via a transmission (not shown). In this case, if the electric motor 1 functions as a generator when the vehicle is decelerated, it can be recovered as regenerative energy in the electric storage device. Further, in the hybrid vehicle, the rotating shaft 4 of the electric motor 1 can be further connected to a crankshaft (not shown) of the internal combustion engine so that it can be used for power generation by the internal combustion engine.

  The rotor unit 3 includes an annular outer circumferential rotor 5 and an annular inner circumferential rotor 6 disposed coaxially inside the outer circumferential rotor 5, and includes the outer circumferential rotor 5 and the inner circumferential surface. The side rotor 6 is rotatable within a set angle range.

  The outer rotor 5 and the inner rotor 6 are formed by, for example, sintered rotor cores 7 and 8 made of sintered metal, and are biased toward the outer periphery of the rotor cores 7 and 8. A plurality of magnet mounting slots 7a, 8a are formed at equal intervals in the circumferential direction. In each of the magnet mounting slots 7a and 8a, two flat plate-like permanent magnets 9 and 9 magnetized in the thickness direction are mounted in parallel. Two permanent magnets 9, 9 mounted in the same magnet mounting slot 7a, 8a are magnetized in the same direction, and a pair of permanent magnets 9 mounted in each adjacent magnet mounting slot 7a, 7a and 8a, 8a. The magnetic poles are set so that the directions of the magnetic poles are opposite to each other. That is, in each of the rotors 5 and 6, a pair of permanent magnets 9 whose outer peripheral side is an N pole and a pair of permanent magnets 9 that are an S pole are alternately arranged in the circumferential direction. A notch 10 for controlling the flow of magnetic flux of the permanent magnet 9 is rotated between the adjacent magnet mounting slots 7a, 7a and 8a, 8a on the outer peripheral surfaces of the rotors 5, 6. It is formed along the axial direction of the children 5 and 6.

  The same number of magnet mounting slots 7a, 8a of the outer rotor 5 and inner rotor 6 are provided, and the permanent magnets 9 of the rotors 5, 6 correspond to each other on a one-to-one basis. Therefore, by making the pair of permanent magnets 9 in each of the magnet mounting slots 7a and 8a of the outer peripheral rotor 5 and the inner peripheral rotor 6 face each other with the same polarity (with different polar arrangement), the rotor unit 3 is able to obtain a field weakening state (see FIGS. 4 and 5B) in which the field of the entire field is most weakened, and the magnet mounting slots 7a of the outer peripheral rotor 5 and the inner peripheral rotor 6. , 8a, the pair of permanent magnets 9 are opposed to each other with different polarities (with the same polarity arrangement), so that the field of the entire rotor unit 3 is most strongly strengthened (see FIGS. 2 and 5). (See (a)) can be obtained.

  In the rotor unit 3, the outer peripheral side rotor 5 and the inner peripheral side rotor 6 are relatively rotated by a rotation operation mechanism 11. The rotation operation mechanism 11 is operated by the hydraulic pressure of the hydraulic circuit shown in FIG. 6, and constitutes a hydraulic actuator of the oil supply apparatus according to the present invention.

  As shown in FIGS. 1 to 4, the rotation operation mechanism 11 is a vane rotor 14 that is spline-fitted to the outer periphery of the rotation shaft 4 so as to be integrally rotated, and an annular shape that is disposed on the outer periphery side of the vane rotor 14 so as to be relatively rotatable. The annular housing 15 is integrally fitted and fixed to the inner peripheral surface of the inner circumferential rotor 6, and the vane rotor 14 is provided on both axial sides of the annular housing 15 and the inner circumferential rotor 6. It is integrally coupled to the outer peripheral rotor 5 via a pair of disk-shaped drive plates 16, 16 straddling the side end portions. Therefore, the vane rotor 14 is integrated with the rotary shaft 4 and the outer peripheral rotor 5, and the annular housing 15 is integrated with the inner peripheral rotor 6.

  In the vane rotor 14, a plurality of vanes 18 projecting radially outward are provided at equal intervals in the circumferential direction on the outer periphery of a cylindrical boss portion 17 that is spline-fitted to the rotary shaft 4. On the other hand, the annular housing 15 is provided with a plurality of concave portions 19 on the inner peripheral surface at equal intervals in the circumferential direction, and the corresponding vanes 18 of the vane rotor 14 are accommodated in the concave portions 19. Each recess 19 is constituted by a bottom wall 20 having an arc surface that substantially matches the rotational trajectory of the tip of the vane 18 and a substantially triangular partition wall 21 that separates the adjacent recesses 19, 19. The vane 18 can be displaced between the one partition wall 21 and the other partition wall 21 during relative rotation of the annular housing 15. In the case of this embodiment, the partition wall 21 also functions as a stopper that restricts the relative rotation of the vane rotor 14 and the annular housing 15 by contacting the vane 18. A seal member 22 is provided along the axial direction at the tip of each vane 18 and the tip of the partition wall 21, and the vane 18, the bottom wall 20 of the recess 19, and the partition wall 21 are provided by these seal members 22. And the outer peripheral surface of the boss portion 17 are liquid-tightly sealed.

  Further, the base portion 15a of the annular housing 15 fixed to the inner peripheral rotor 6 is formed in a cylindrical shape having a constant thickness, and is also provided with respect to the inner peripheral rotor 6 and the partition wall 21 as shown in FIG. Projects outward in the axial direction. Each end projecting outward of the base portion 15a is slidably held in an annular guide groove 16a formed in the drive plate 16, and the annular housing 15 and the inner peripheral rotor 6 are connected to the outer peripheral rotor. 5 and the rotating shaft 4 are supported in a floating state.

  The drive plates 16 and 16 on both sides connecting the outer rotor 5 and the vane rotor 14 are slidably in close contact with both side surfaces (both end surfaces in the axial direction) of the annular housing 15, and the side of each recess 19 of the annular housing 15. Respectively. Therefore, each recessed part 19 forms the independent space part by the boss | hub part 17 of the vane rotor 14, and the drive plates 16 and 16 of both sides, and this space part becomes the introduction space 23 into which oil is introduced. Each introduction space 23 is divided into two chambers by the corresponding vanes 18 of the vane rotor 14, and one room is an advance side working chamber 24 and the other room is a retard side working chamber 25. The advance side working chamber 24 rotates the inner circumferential side rotor 6 relative to the outer circumferential side rotor 5 in the advance direction by the pressure of the oil introduced therein. The inner rotor 6 is rotated relative to the outer rotor 5 in the retarding direction by the pressure of the oil introduced into the outer periphery. In this case, “advance angle” means that the inner circumferential rotor 6 is advanced relative to the outer circumferential rotor 5 in the rotational direction of the electric motor 1 indicated by an arrow R in FIGS. 2 and 4. “Angle” means that the inner rotor 6 is advanced to the opposite side of the rotation direction R of the electric motor 1 with respect to the outer rotor 5.

  In addition, oil is supplied to and discharged from each of the advance side working chambers 24 and the retard side working chambers 25 through the rotary shaft 4. Specifically, the advance side working chamber 24 is connected to the advance side supply / discharge passage 26 of the hydraulic circuit shown in FIG. 6, and the retard side operation chamber 25 is connected to the retard side supply / discharge passage 27 of the hydraulic circuit. Although connected, a part of the advance side supply / exhaust passage 26 and the retard side supply / exhaust passage 27 are, as shown in FIG. 1, passage holes 26a formed along the axial direction of the rotary shaft 4, respectively. 27a. The end portions of the passage holes 26a and 27a are connected to annular grooves 26b and 27b formed at positions offset in the axial direction of the outer peripheral surface of the rotating shaft 4, and the annular grooves 26b and 27b are connected to the vane rotor 14. Are connected to a plurality of conduction holes 26c,..., 27c. Each conduction hole 26c of the advance side supply / discharge passage 26 connects the annular groove 26b and each advance side working chamber 24, and each conduction hole 27c of the retard side supply / exhaust passage 27 connects to the annular groove 27b and each retard side. The working chamber 25 is connected.

Here, in the case of the electric motor 1 of this embodiment, when the inner circumferential rotor 6 is at the most retarded position with respect to the outer circumferential rotor 5, the outer circumferential rotor 5 and the inner circumferential rotor 6 are permanent. The magnets 9 are opposed to each other with different polarities and are in a strong field state (see FIGS. 2 and 5A), and the inner circumferential rotor 6 is at the most advanced position with respect to the outer circumferential rotor 5. Sometimes, the permanent magnets 9 of the outer rotor 5 and the inner rotor 6 are set so as to face each other with the same poles and to have a field weakening state (see FIGS. 4 and 5B). Yes.
The electric motor 1 can arbitrarily change the state of the strong field and the state of the weak field by controlling the supply and discharge of hydraulic oil to and from the advance side working chamber 24 and the retard side working chamber 25. Thus, when the strength of the magnetic field is changed, the induced voltage constant is changed accordingly, and as a result, the characteristics of the electric motor 1 are changed. That is, if the induced voltage constant increases due to the strong field, the allowable rotational speed at which the motor 1 can be operated decreases, but the maximum torque that can be output increases. Conversely, if the induced voltage constant decreases due to the weak field, Although the maximum torque that can be output from the electric motor 1 decreases, the allowable rotational speed at which the motor 1 can operate increases.

  FIG. 6 is a hydraulic circuit diagram showing the vehicle oil supply device 13 according to the present invention. The oil supply device 13 includes an electric oil pump 32 as a hydraulic pressure supply source, and oil discharged from the electric oil pump 32 is supplied to the high-pressure oil passage and the low-pressure oil passage. The electric oil pump 32 includes a high-pressure pump mechanism 50 and a low-pressure pump mechanism 51, and these pump mechanisms 50 and 51 are driven to rotate by a common output shaft of an electric motor 52. The high pressure pump mechanism 50 is connected to a line pressure passage 33 that is a high pressure oil passage, and the low pressure pump mechanism 51 is connected to a lubrication / cooling passage 34 (low pressure oil passage) that is a low pressure oil passage.

  A pressure regulating valve 35 that regulates the supply pressure to the line pressure passage 33 is interposed between the high pressure pump mechanism 50 and the line pressure passage 33, and oil discharged as an excess by the pressure regulating valve 35 is drain passage. 53 is supplied to the lubrication / cooling passage 34. An oil temperature sensor 67 (temperature detection means) that detects the temperature of oil discharged from the high-pressure pump mechanism 50 is provided in the vicinity of the pressure regulating valve 35 in the line pressure passage 33, and is detected by the temperature sensor 67. A temperature signal is input to the controller 38.

The line pressure passage 33 is connected to the advance side supply / discharge passage 26 and the retard side supply / discharge passage 27 of the rotational operation mechanism 11 of the electric motor 1 via a spool type flow switching valve 37. The flow path switching valve 37 distributes the hydraulic oil introduced into the line pressure passage 33 to the advance side supply / discharge passage 26 and the retard side supply / exhaust passage 27, and to the advance side supply / discharge passage 26 and the retard side supply / discharge passage. Unnecessary hydraulic oil is discharged to the drain passage 36 through the passage 27, and these operations are performed according to the position of the spool that is hydraulically operated. The operation pressure of the flow path switching valve 37 is created by an electromagnetic pressure regulating valve 39 based on the pressure in the line pressure passage 33, and the pressure regulating valve 39 is controlled by a controller 38. Therefore, the phase control of the rotor unit 3 by the rotation operation device 11 is performed through the control of the pressure regulating valve 39 by the controller 38.
When the phase of the rotor unit 3 is not changed, oil is supplied through the line pressure passage 33 so as to compensate for oil leakage in the rotation operation mechanism 11.

  Further, the lubrication / cooling passage 34 connected to the low-pressure pump mechanism 51 includes a lubricating passage 51A that lubricates the electric motor 1 and surrounding power transmission system devices, and a working oil for the cooling portion 1a in the electric motor 1 and surrounding devices. Is branched to a cooling passage 51B that supplies the coolant as a coolant, and the supply of hydraulic oil to the cooling passage 51B is appropriately controlled by a control valve 56. In FIG. 6, 57 is an oil cooler pressure control valve, and 58 is an oil cooler.

Incidentally, the controller 38 for controlling the electric oil pump 32 has the following configurations (a) to (f) for controlling the driving speed of the electric motor 52 when the rotation operation mechanism 11 of the electric motor 1 is in an inoperative state. (See FIG. 7).
(A) Leakage flow rate calculation means 60 for calculating the flow rate Qleak of oil leaking from the operation mechanism 11 when the rotation operation mechanism 11 is not operated.
(B) Low pressure required flow rate calculation means 61 for calculating the oil flow rate Qcool required in the lubrication / cooling passage 34.
(C) Total required flow rate calculation means 62 that calculates the total required flow rate Qleak + Qcool of oil by adding the calculation results of the leak flow rate calculation means 60 and the low pressure required flow rate calculation means 61 when the rotation operation mechanism 11 is not operating.
(D) Necessary motor speed calculation means 63 for calculating the necessary rotational speed N1 of the electric motor 52 for obtaining the total necessary flow rate Qleak + Qcool.
(E) Threshold motor speed calculation means 64 for calculating the threshold rotation speed N2 of the electric motor 52 at which the oil discharge flow rate at the high-pressure pump mechanism 50 is substantially the same as the oil leak flow rate Qleak of the rotation operation mechanism 11.
(F) Drive control means 65 that receives the calculation results of the necessary motor speed calculation means 63 and the threshold motor speed calculation means 64 and controls the drive speed of the electric motor 52 according to the calculation results.

  For example, the leak flow rate calculation means 60 stores the correlation map 1 between the oil temperature t and the leak flow rate Qleak as shown in FIG. 8 in the storage unit of the controller 38, and leaks corresponding to the detected temperature t detected by the oil temperature sensor 37. The flow rate Qleak is obtained with reference to the correlation map 1.

  The low pressure required flow rate calculation means 61 receives detection signals such as the temperature of the cooling section 1a in the electric motor 1 and the operating speed of the equipment to be lubricated through a sensor (not shown) to the controller 38, and based on these detection signals, lubrication / An oil flow rate Qcool required in the cooling passage 34 is calculated. Also in this case, the flow rate Qcool may be obtained by referring to a correlation map.

  The required motor speed calculation means 63 receives the data of the total required flow rate Qleak + Qcool obtained by the total required flow rate calculation means 62, and sums the discharge flow rate Ql of the low pressure pump mechanism 51 and the discharge flow rate Qh of the high pressure pump mechanism 50. The required rotational speed N1 of the electric motor 52 is determined so that the oil flow rate Ql + Qh becomes equal to the current total required flow rate Qleak + Qcool. Specifically, for example, a correlation map 2 between the total discharge flow rate Ql + Qh of the electric oil pump 32 and the required rotational speed N1 of the electric motor 52 as shown in FIG. 9 is stored in the storage unit of the controller 38, and Ql + Qh = Qleak + Qcool. As a result, the necessary rotational speed N1 corresponding to the total necessary flow rate calculation data Qleak + Qcool is obtained with reference to the correlation map 2. In this case, correlation data between the total discharge flow rate Ql + Qh and the necessary rotational speed N1 in the correlation map 2 is provided for each oil temperature (for example, every t1, t2, t3 (t1> t2> t3)), and the oil temperature sensor 37. The required rotational speed N1 is obtained using the correlation data corresponding to the detected temperature.

  The threshold motor speed calculation means 64 receives the leak flow rate Qleak data of the rotation operation mechanism 11 obtained by the leak flow calculation means 60, and the discharge flow rate Qh of the high pressure pump mechanism unit 50 is the current leak flow rate of the rotation operation mechanism 11. A threshold rotational speed N2 that is the rotational speed of the electric motor 52 when equal to Qleak is obtained. Specifically, for example, the correlation map 3 between the discharge flow rate Qh of the high-pressure pump mechanism 50 and the threshold rotational speed N2 of the electric motor 52 as shown in FIG. 10 is stored in the storage unit of the controller 38, and Qleak = Qh As a result, the threshold rotational speed N2 corresponding to the leak flow rate calculation data Qleak is obtained with reference to the correlation map 3. Also in this case, correlation data between the discharge flow rate Qh and the threshold rotation speed N2 in the correlation map 3 is provided for each oil temperature (for example, every t1, t2, t3 (t1> t2> t3)), and the oil temperature sensor 37. The threshold rotation speed N2 is obtained using the correlation data corresponding to the detected temperature.

  The drive control means 65 compares the calculated data N1 of the necessary motor speed calculating means 63 with the calculated data N2 of the threshold motor speed calculating means 64, and when N1 ≧ N2, that is, the electric motor 52 is driven at the required rotational speed N1. If there is no shortage in compensating for the leakage flow rate Qleak of the rotation operation mechanism 11 when driven, the drive speed of the electric motor 52 is controlled to the required rotation speed N1, and when N1 <N2, that is, the required rotation When the electric motor 52 is driven at the speed N1, if there is a shortage in compensating for the leakage flow rate Qleak of the rotation operation mechanism 11, the driving speed of the electric motor 52 is set to a set rotational speed equal to or higher than the threshold rotational speed N2, for example, Control is made to the same rotational speed as the threshold rotational speed N2. In the following description, it is assumed that the set rotational speed is the same rotational speed as the threshold rotational speed N2.

Next, specific control of the electric oil pump 32 when the rotation operation mechanism 11 is in an inoperative state will be described with reference to the flowchart of FIG.
First, in step S101, it is determined whether or not the rotation operation mechanism 11 is in an operating state. When the rotation operation mechanism 11 is in an operation state, the control operation is skipped and the description is omitted. When the rotary operation mechanism 11 is in a non-operating state, the process proceeds to step S102, and the detection data of the oil temperature sensor 67 is read.
Subsequently, in step S103, the leak flow rate Qleak corresponding to the current oil temperature is obtained with reference to the correlation map 1, and in step S104, the current flow is required in the lubrication / cooling passage 34 with reference to a map (not shown). Determine the oil flow Qcool. In the next step S105, the total required flow rate Qleak + Qcool is obtained by adding the leak flow rate Qleak obtained in steps S103 and S104 and the necessary flow rate Qcool.
In the next step S106, the correlation map 2 is referred to obtain the required total rotational flow rate N1 of the electric motor 52 corresponding to the current total required flow rate Qleak + Qcool and the oil temperature, and in the subsequent step S107, the correlation map 3 is referred to. Then, the threshold rotational speed N2 of the electric motor 52 corresponding to the current leak flow rate Qleak and the oil temperature is obtained.
Then, in step S108, it is determined whether or not the required rotational speed N1 of the electric motor 52 obtained in step S106 is equal to or higher than the threshold rotational speed N2 obtained in step S107, and the required rotational speed N1 is equal to or higher than the threshold rotational speed N2. When the required rotational speed N1 is smaller than the threshold rotational speed N2, the process proceeds to step S110. When the process proceeds to step S109, the drive of the electric motor 52 is controlled so that the drive rotation speed becomes the necessary rotation speed N1. At this time, in the pressure regulating valve 39, the oil having a flow rate obtained by subtracting the leak flow rate Qleak in the rotation operation mechanism 11 out of the flow rate of oil discharged from the high pressure pump mechanism unit 50 is supplied to the lubrication / cooling passage 34. The When the process proceeds to step S110, the drive of the electric motor 52 is controlled so that the drive rotation speed becomes the threshold rotation speed N2.

As described above, in this oil supply device 13, basically, the electric motor 52 is driven at the required rotational speed N1 so that the total required flow rate Qleak + Qcool on the low pressure side and the high pressure side is obtained, and the required rotational speed N1 is a threshold value. Since it is driven at the threshold rotational speed N2 only when the rotational speed is less than the rotational speed N2, the power loss of the electric oil pump 32 can be reliably suppressed with an extremely simple configuration.
In particular, in the oil supply device 13, when the required rotational speed N 1 is equal to or higher than the threshold rotational speed N 2, surplus oil discharged from the high-pressure pump mechanism 50 is introduced into the lubrication / cooling passage 34 via the pressure regulating valve 39. The electric oil pump 32 is driven so that the total flow rate of oil obtained by adding the flow rate introduced here and the discharge flow rate from the low-pressure pump mechanism 51 satisfies the required flow rate Qcool. Most of the oil produced can be used effectively on either the high pressure side or the low pressure side.
Therefore, according to this oil supply device 13, it is possible to achieve both a reduction in power consumption of the electric motor 52 and a reduction in manufacturing cost at a high level.

  Further, in the oil supply device 13, the oil temperature sensor 67 detects the temperature of the oil discharged from the high-pressure pump mechanism 50, and obtains the leak flow rate of the rotation operation mechanism 11 reflecting the current temperature state of the oil. Thus, the calculation error of the leak flow rate Qleak due to the oil temperature change can be reduced.

  Further, in this oil supply device 13, the required rotational speed N1 of the electric motor 52 and the threshold rotational speed N2 of the electric motor 52 for obtaining the total required flow rate Qleak + Qcool are set according to the temperature of the oil detected by the oil temperature sensor 67. Therefore, the calculation error between the required rotational speed N1 and the threshold rotational speed N2 due to the change in oil temperature can be reduced.

  Further, in this embodiment, the rotation operation mechanism 11 of the electric motor 1 is controlled by the oil supply device 13 described above, so that the electric oil pump 32 is reduced in power consumption and the induction of the electric motor 1 is induced. The voltage constant can be stably maintained.

  In addition, this invention is not limited to said embodiment, A various design change is possible in the range which does not deviate from the summary. For example, in the above embodiment, the rotation operation mechanism 11 of the electric motor 1 is connected to the line pressure passage 33 of the oil supply device 13, but hydraulic actuators that use oil through the line pressure passage 33 are other than the electric motor 1. Various drive devices for vehicles may be used.

1 is a cross-sectional view of a main part of an electric motor used in an embodiment of the present invention. The side view which abbreviate | omitted some components of the rotor unit controlled to the most retarded angle position of the electric motor of the embodiment. The disassembled perspective view of the rotor unit of the electric motor of the embodiment. The side view which abbreviate | omitted some components of the rotor unit controlled to the most advanced angle position of the electric motor of the embodiment. The figure (a) which shows typically the strong field state where the permanent magnet of the inner circumference side rotor and the permanent magnet of the outer circumference side rotor are arranged in the same polarity, and the permanent magnet and outer circumference side rotation of the inner circumference side rotor The figure which also described the figure (b) which shows typically the field-weakening state by which the permanent magnet of a child was arrange | positioned differently. The hydraulic circuit diagram of the oil supply apparatus of the embodiment. The functional block diagram of the oil supply apparatus of the embodiment. The leak flow rate Qleak-oil temperature t map used in the embodiment. Necessary rotational speed N1 used in the same embodiment-Total required flow rate Ql + Qh map. The threshold rotational speed N2 used in the same embodiment-high pressure side required flow rate Qh map. The flowchart which shows the flow of the motor drive control of the oil supply apparatus of the embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Electric motor 5 ... Outer peripheral side rotor 6 ... Inner peripheral side rotor 9 ... Permanent magnet 11 ... Turning operation mechanism (hydraulic actuator, phase change means)
DESCRIPTION OF SYMBOLS 13 ... Oil supply apparatus 32 ... Electric oil pump 33 ... Line pressure passage 34 ... Lubrication / cooling passage (low pressure oil passage)
35 ... Pressure regulating valve 50 ... High pressure pump mechanism 51 ... Low pressure pump mechanism 52 ... Electric motor 60 ... Leak flow rate calculation means 61 ... Low pressure required flow rate calculation means 62 ... Total required flow rate calculation means 63 ... Required motor speed calculation means 64 ... Threshold Motor speed calculation means 65 ... drive control means 67 ... temperature sensor (temperature detection means)

Claims (6)

An electric oil pump having a high pressure pump mechanism and a low pressure pump mechanism driven by a common electric motor;
A line pressure passage for supplying oil discharged from the high-pressure pump mechanism to a hydraulic actuator of a vehicle;
A low-pressure oil passage for supplying oil discharged from the low-pressure pump mechanism to a low-pressure oil utilization part of a vehicle device;
A pressure regulating valve that regulates oil discharged from the high-pressure pump mechanism and supplied to the line pressure passage to a set pressure, and supplies surplus oil to the low-pressure oil passage;
A leakage flow rate calculating means for calculating a flow rate of oil leaking from the hydraulic actuator when the hydraulic actuator is not operated;
A low pressure required flow rate calculating means for calculating a flow rate of oil required in the low pressure oil passage;
A total required flow rate calculating means for calculating a total required flow rate of oil from the calculation results of the leak flow rate calculating means and the low pressure required flow rate calculating means when the hydraulic actuator is not operated;
Required motor speed calculating means for calculating a required rotational speed of the electric motor for obtaining the total required flow rate;
Threshold motor speed calculation means for calculating a threshold rotation speed of the electric motor at which the oil discharge flow rate in the high-pressure pump mechanism is substantially the same as the oil leak flow rate from the hydraulic actuator;
Based on the calculation results of the necessary motor speed calculating means and the threshold motor speed calculating means, when the required rotational speed of the electric motor for obtaining the total required flow rate is not less than the threshold rotational speed when the hydraulic actuator is not operated. When the required rotation speed of the electric motor for driving the electric motor at the required rotation speed and obtaining the total required flow rate is smaller than the threshold rotation speed, the electric motor is driven at a set speed equal to or higher than the threshold rotation speed. Drive control means for driving;
An oil supply device for a vehicle, comprising:   The pressure regulating valve has a flow rate obtained by subtracting a leak flow rate of the hydraulic actuator from a flow rate of oil discharged from the high-pressure pump mechanism when the electric motor is driven at the required rotational speed when the hydraulic actuator is not operated. 2. The vehicle oil supply device according to claim 1, wherein the vehicle oil supply device is set to be supplied to a low-pressure oil passage.   The oil supplied to the line pressure passage is used for operation of a hydraulic actuator of a drive mechanism, and the oil supplied to the low pressure oil passage is used for at least one of cooling and lubrication of vehicle equipment. Item 3. The vehicle oil supply device according to any one of Items 1 and 2. Temperature detecting means for detecting the temperature of oil discharged from the high-pressure pump mechanism,
The vehicle oil supply device according to any one of claims 1 to 3, wherein the leak flow rate calculation means calculates a leak flow rate based on a temperature detected by the temperature detection means. Temperature detecting means for detecting the temperature of oil discharged from the high-pressure pump mechanism,
The said required motor speed calculation means and a threshold motor speed calculation means calculate the required rotational speed and threshold rotational speed of an electric motor based on the temperature detected by the said temperature detection means, Any one of Claims 1-4 characterized by the above-mentioned. The vehicle oil supply device according to claim 1.   The hydraulic actuator is disposed on the outer circumferential side of the inner circumferential rotor on which a permanent magnet is disposed along the circumferential direction, and is coaxially and relatively rotatable on the outer circumferential side of the inner circumferential rotor, A phase change that changes the relative phase between the outer peripheral rotor on which the permanent magnets are arranged along the circumferential direction, and the inner peripheral rotor and the outer peripheral rotor are relatively rotated by hydraulic pressure. The vehicle oil supply device according to any one of claims 1 to 5, wherein the phase changing means of the electric motor is provided.

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