EP3306095B1 - Oil supply device and method of controlling electric oil pump - Google Patents
Oil supply device and method of controlling electric oil pump Download PDFInfo
- Publication number
- EP3306095B1 EP3306095B1 EP16799829.3A EP16799829A EP3306095B1 EP 3306095 B1 EP3306095 B1 EP 3306095B1 EP 16799829 A EP16799829 A EP 16799829A EP 3306095 B1 EP3306095 B1 EP 3306095B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- oil
- volumetric change
- electric oil
- rotary volumetric
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 238000000034 method Methods 0.000 title claims description 14
- 239000003921 oil Substances 0.000 description 85
- 238000001816 cooling Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 238000005086 pumping Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 2
- 230000000750 progressive effect Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 238000007599 discharging Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000037452 priming Effects 0.000 description 1
- 230000007420 reactivation Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/02—Stopping, starting, unloading or idling control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
- F04C13/002—Pumps for particular liquids for homogeneous viscous liquids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/20—Fluid liquid, i.e. incompressible
- F04C2210/206—Oil
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/20—Rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/40—Electric motor
Definitions
- the present invention relates to an oil supply device in which negative pressure generated inside a pump chamber is reduced or eliminated when an electric oil pump is to be shut down, and a method of controlling an electric oil pump.
- Oil supply devices used for cooling a motor of a hybrid car, a generator, and the like employ an electric oil pump.
- Rotary volumetric change pumps are widely used as the electric oil pump (for example, refer to Patent Literature 1).
- FIG. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) are operation diagrams for describing an operation of the rotary volumetric change pump in which a rotor rotates, in the order of Fig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) .
- the drawings illustrate an example of steps of intaking, compressing, and discharging oil 40 performed in one pump chamber. Regions filled with the oil are indicated with oblique lines.
- a rotary volumetric change pump 20 is provided with an inner rotor 21 and an outer rotor 22 of which the numbers of teeth are different from each other.
- the inner rotor 21 serves as an external gear
- the outer rotor 22 serves as an internal gear
- each of the rotors has a tooth form formed based on a trochoid curve.
- the inner rotor 21 has four teeth
- the outer rotor 22 has five teeth.
- a circumscribed portion of the outer rotor 22 is accommodated in a round casing (not illustrated).
- Fig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) illustrates an example of clockwise rotation as indicated with the arrow.
- the rotary volumetric change pump 20 is driven when a brushless DC motor or the like causes the inner rotor 21 to rotate.
- the operation of the motor is configured to be controlled by an electric oil pump controller in response to a command from a host controller (for example, refer to Patent Literature 1).
- the oil 40 is taken into the pump chamber through the intake side 31 and negative pressure is generated inside the pump chamber.
- the viscosity of the oil 40 increases and the oil 40 is unlikely to be taken in. Consequently, higher negative pressure is generated.
- US 2001/055528 A1 discloses a progressive cavity pumping system for use in pumping an associated aggregate material.
- the progressive cavity pumping system includes a pump housing, a rotor member operatively received in the pump housing, a prime mover coupled to the rotor member, and a controlling means for actuating the prime mover.
- JP 2004-353624 A discloses a control device for a motor-driven liquid pump configured to detect rotational frequency of the liquid pump to determine whether the pump is biting foreign matter. If it is determined that foreign matter has entered the pump, the control device rotates the electric motor in a reverse direction followed by at least one rotation in the forward direction.
- JP H06 30482 U discloses an inner gear pump including a reservoir to store lubricating oil when the pump is not active, so as to speed up priming of the pump upon reactivation.
- an object of the present invention is to provide an oil supply device in which negative pressure inside a pump chamber is reduced or eliminated when an electric oil pump is shut down, thereby preventing air from entering the pump chamber and allowing oil to be supplied or to circulate smoothly, and a method of controlling an electric oil pump.
- an oil supply device according to the subject-matter of claim 1.
- the predetermined angle, by which the rotary volumetric change pump is caused to rotate in the direction opposite to the rotation direction during oil supply may be 360 degrees with respect to the inner rotor.
- the kinematic viscosity coefficient of oil to be supplied using the rotary volumetric change pump may be equal to or higher than 1,000 mm 2 /s.
- the oil supply device and the method of controlling an electric oil pump according to the present invention are employed, it is possible to avoid a state in which negative pressure is high inside a pump chamber of the rotary volumetric change pump when the electric oil pump is shut down, and it is possible to prevent air from entering the pump chamber through an intake side. Therefore, when being actuated afterward, the electric oil pump has an effect that a sufficient amount of oil can be smoothly applied immediately after the electric oil pump is actuated.
- Fig. 1 is a block diagram of an oil supply device 10 of the present invention.
- Fig. 2 illustrates a simplified diagram of an electric oil pump showing the internal structure.
- the oil supply device 10 of the present invention causes cooling oil 40 to circulate, thereby cooling a cooling subject device 17 such as an electric motor and a generator.
- the oil supply device 10 includes a rotary volumetric change pump 20 and an electric oil pump 11 provided with a motor 12 which operates the rotary volumetric change pump 20.
- the rotary volumetric change pump 20 has a structure in which an inner rotor 21 serves as an external gear, an outer rotor 22 serves as an internal gear, and each of the rotors has a tooth form formed based on a trochoid curve.
- a circumscribed portion of the outer rotor 22 is accommodated in a round casing.
- the centers of the inner rotor 21 and the outer rotor 22 do not coincide with each other, thereby being provided with a certain eccentricity.
- a gap between the inner rotor 21 and the outer rotor 22 becomes the inside of a pump chamber.
- the gap which is the inside of the pump chamber is widened or narrowed, thereby allowing operation of a pump.
- the intake side 31 of the pump chamber and the discharge side 33 of the pump chamber are the places which are each surrounded by the bold line in Fig. 2 .
- the cooling oil 40 accumulated in an oil sump of an oil pan 15 is suctioned up through an intake port 30 by the rotary volumetric change pump 20, and the cooling oil 40 is pressure-fed to the cooling subject device 17, such as the electric motor and the generator, through a discharge port 32 via an oil cooler 16.
- the oil cooler 16 radiates heat of the oil 40 passing through. Then, the oil 40 which has cooled the cooling subject device 17 is configured to return to the oil pan 15.
- the rotary volumetric change pump 20 is operated when a movement of the motor 12 is transmitted to the inner rotor 21, and the operation of the motor 12 is controlled by an electric oil pump controller 13.
- a host controller 14 sends a control signal to this electric oil pump controller 13.
- Fig. 3 is a flow chart of control over the motor 12 conducted by the electric oil pump controller 13.
- Step S10 at the start work is performed to turn on power, for example, an engine of a vehicle is started.
- Step S11 the electric oil pump controller 13 receives a motor control signal. Then, in Step S12, it is determined whether or not the received control signal has changed.
- Step S12 when the control signal has not changed, the state is retained as it is, and the electric oil pump controller 13 waits for reception of a control signal again.
- Step S13 the process proceeds to Step S13, and it is determined whether or not the control signal is for operation or not.
- Step S13 when it is determined that the control signal is for operation, the process proceeds to Step S14, and the motor 12 is caused to rotate normally.
- Step S13 when it is determined that the control signal is not for operation, that is, in a case of a control signal for shutdown, the process proceeds to Step S15, and the motor 12 is caused to temporarily stop. Furthermore, the process proceeds to Step S16, and the motor 12 is caused to rotate reversely by a certain amount of rotation, thereby eliminating the negative pressure inside the pump chamber. Lastly, the process proceeds to Step S17, and the motor 12 is completely shut down.
- the angle of the reverse rotation required to eliminate the negative pressure is determined depending on various factors such as the viscosity coefficient of oil and the shapes of rotors. Therefore, the angle varies case by case. However, in order to suppress generation of excessive negative pressure, it is considered that a sufficient effect can be obtained when the inner rotor 21 is caused to rotate reversely by 360 degrees.
- the present invention is characterized in that after it is determined that a control signal is not for operation any longer, a step is performed at all times, in which the motor is caused to temporarily stop, the motor is caused to rotate reversely, and the motor is then completely shut down. If it is intended to determine whether or not the motor is to be caused to rotate reversely in accordance with the magnitude of negative pressure inside the pump chamber, the oil pressure has to be measured, so that there is a need to separately provide a device therefor.
- the motor is caused to rotate reversely at all times, and the angle of the reverse rotation is set in advance within a range in which a sufficient effect can be obtained and the circulation of oil is not affected. Accordingly, even though no extra device is provided, it is possible to achieve a sufficient effect.
- the configuration of the present invention is not limited to only oil pumps used for cooling a device and can also be widely utilized in devices in which fluid having a high viscosity coefficient is supplied and circulates.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Description
- The present invention relates to an oil supply device in which negative pressure generated inside a pump chamber is reduced or eliminated when an electric oil pump is to be shut down, and a method of controlling an electric oil pump.
- Oil supply devices used for cooling a motor of a hybrid car, a generator, and the like employ an electric oil pump. Rotary volumetric change pumps are widely used as the electric oil pump (for example, refer to Patent Literature 1).
- The operation of a rotary volumetric change pump is disclosed in Patent Literature 2, and the operation will be described simply using the drawings.
Fig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) are operation diagrams for describing an operation of the rotary volumetric change pump in which a rotor rotates, in the order ofFig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) . Here, the drawings illustrate an example of steps of intaking, compressing, and dischargingoil 40 performed in one pump chamber. Regions filled with the oil are indicated with oblique lines. - A rotary
volumetric change pump 20 is provided with aninner rotor 21 and anouter rotor 22 of which the numbers of teeth are different from each other. In the structure, theinner rotor 21 serves as an external gear, theouter rotor 22 serves as an internal gear, and each of the rotors has a tooth form formed based on a trochoid curve. InFig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) , theinner rotor 21 has four teeth, and theouter rotor 22 has five teeth. However, this is merely an example, and the numbers of teeth may vary. A circumscribed portion of theouter rotor 22 is accommodated in a round casing (not illustrated). The centers of theinner rotor 21 and theouter rotor 22 do not coincide with each other, thereby being configured to be provided with a certain eccentricity. In such a configuration, when rotation is applied to theinner rotor 21, theouter rotor 22 rotates with a delay in the same direction.Fig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) illustrates an example of clockwise rotation as indicated with the arrow. - When the
inner rotor 21 and theouter rotor 22 rotate, gears mesh with each other at a location where the distance between both the gears is short, and a gap is formed at a location where the distance between both the gears is long. When the gap is widened or narrowed due to such movement, theoil 40 is forcibly suctioned into the gap or is discharged from the gap, thereby allowing operation of a pump. - In
Fig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) , when theinner rotor 21 and theouter rotor 22 rotate clockwise, theoil 40 starts to be taken into a pump chamber through anintake side 31 as illustrated inFig. 4(a) , and when theinner rotor 21 and theouter rotor 22 further rotate,more oil 40 is taken in as illustrated inFig. 4(b) . - Next, in
Fig. 4(c) , theoil 40 is in the maximum intake state, and therefrom a compressing step illustrated inFig. 4(d) and thereafter is started. Lastly, as illustrated inFig. 4(e) , theoil 40 is discharged from the pump chamber through adischarge side 33 and is pressure-fed toward acooling subject device 17. - The rotary
volumetric change pump 20 is driven when a brushless DC motor or the like causes theinner rotor 21 to rotate. The operation of the motor is configured to be controlled by an electric oil pump controller in response to a command from a host controller (for example, refer to Patent Literature 1). - When the rotary
volumetric change pump 20 is used, theoil 40 is taken into the pump chamber through theintake side 31 and negative pressure is generated inside the pump chamber. Particularly, when the oil temperature is low, the viscosity of theoil 40 increases and theoil 40 is unlikely to be taken in. Consequently, higher negative pressure is generated. - When being in circumstances in which the negative pressure inside the pump chamber is high as described above, if the rotary
volumetric change pump 20 is shut down, there are cases where air enters the pump chamber due to the influence of the negative pressure. Empirically, it has been ascertained that when the kinematic viscosity coefficient of oil is equal to or higher than approximately 1,000 mm2/s, the negative pressure inside the pump chamber reaches a state of having dropped 30 kPa from atmospheric pressure, and air enters the pump chamber through a seal portion. When the pump is restarted in a state in which air has entered the pump chamber, it is difficult for theoil 40 to be supplied or to circulate smoothly until the oil temperature of theoil 40 sufficiently rises and the kinematic viscosity coefficient of the oil is lowered. - Actual examples, in which such circumstances are likely to be caused, include a case where after a parked vehicle is exposed to a low temperature for many hours, an engine is started, and the engine is instantly shut down. Specifically, the examples include circumstances where after a vehicle is exposed to outside air overnight in a cold region or the like, an engine is started in the early morning, and the engine is shut down before the engine is sufficiently warmed up. It is generally considered that an electric oil pump is started and shut down in response to a start and a shutdown of an engine.
- In such circumstances, above all, since the vehicle has been exposed to outside air overnight, oil is in a state in which the viscosity coefficient is high compared to when being at an ordinary temperature. Accordingly, since the oil is unlikely to be taken in smoothly when the engine is started, significant negative pressure is generated on the intake side of the pump chamber compared to when being at an ordinary temperature. If the engine is shut down in a state in which such negative pressure is applied, excessively low pressure is applied to the intake side of the pump chamber compared to atmospheric pressure. Consequently, in some cases, air enters the pump chamber through the intake side.
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US 2001/055528 A1 discloses a progressive cavity pumping system for use in pumping an associated aggregate material. The progressive cavity pumping system includes a pump housing, a rotor member operatively received in the pump housing, a prime mover coupled to the rotor member, and a controlling means for actuating the prime mover. -
JP 2004-353624 A -
JP H06 30482 U -
- [Patent Literature 1]
Japanese Unexamined Patent Application Publication No.2014-131453 - [Patent Literature 2]
Japanese Unexamined Patent Application Publication No.2002-339874 - In consideration of the foregoing circumstances, an object of the present invention is to provide an oil supply device in which negative pressure inside a pump chamber is reduced or eliminated when an electric oil pump is shut down, thereby preventing air from entering the pump chamber and allowing oil to be supplied or to circulate smoothly, and a method of controlling an electric oil pump.
- In order to achieve the object, according to the present invention, there is provided an oil supply device according to the subject-matter of claim 1.
- In addition, according to the present invention, there is provided a method of controlling an electric oil pump according to the subject-matter of claim 4.
- Here, in the oil supply device and the method of controlling an electric oil pump, the predetermined angle, by which the rotary volumetric change pump is caused to rotate in the direction opposite to the rotation direction during oil supply, may be 360 degrees with respect to the inner rotor. In addition, the kinematic viscosity coefficient of oil to be supplied using the rotary volumetric change pump may be equal to or higher than 1,000 mm2/s.
- When the oil supply device and the method of controlling an electric oil pump according to the present invention are employed, it is possible to avoid a state in which negative pressure is high inside a pump chamber of the rotary volumetric change pump when the electric oil pump is shut down, and it is possible to prevent air from entering the pump chamber through an intake side. Therefore, when being actuated afterward, the electric oil pump has an effect that a sufficient amount of oil can be smoothly applied immediately after the electric oil pump is actuated.
-
-
Fig. 1 is a block diagram of an oil supply device of the present invention. -
Fig. 2 illustrates a simplified diagram of an electric oil pump showing the internal structure. -
Fig. 3 is a flow chart of control over a motor conducted by the electric oil pump controller. -
Fig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) are operation diagrams for describing an operation of a rotary volumetric change pump in which a rotor rotates, in the order ofFig. 4(a), Fig. 4(b), Fig. 4(c), Fig. 4(d) and Fig. 4(e) . - Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.
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Fig. 1 is a block diagram of anoil supply device 10 of the present invention. In addition,Fig. 2 illustrates a simplified diagram of an electric oil pump showing the internal structure. Theoil supply device 10 of the present invention causes coolingoil 40 to circulate, thereby cooling a coolingsubject device 17 such as an electric motor and a generator. Theoil supply device 10 includes a rotaryvolumetric change pump 20 and anelectric oil pump 11 provided with amotor 12 which operates the rotaryvolumetric change pump 20. - Similar to rotary volumetric change pumps in the related art, the rotary
volumetric change pump 20 has a structure in which aninner rotor 21 serves as an external gear, anouter rotor 22 serves as an internal gear, and each of the rotors has a tooth form formed based on a trochoid curve. A circumscribed portion of theouter rotor 22 is accommodated in a round casing. The centers of theinner rotor 21 and theouter rotor 22 do not coincide with each other, thereby being provided with a certain eccentricity. A gap between theinner rotor 21 and theouter rotor 22 becomes the inside of a pump chamber. When each of the rotors rotates, the gap which is the inside of the pump chamber is widened or narrowed, thereby allowing operation of a pump. A place, at which the gap is widened when theinner rotor 21 and theouter rotor 22 rotate, becomes anintake side 31 of the pump chamber, and a place at which the gap is narrowed becomes adischarge side 33 of the pump chamber. Theintake side 31 of the pump chamber and thedischarge side 33 of the pump chamber are the places which are each surrounded by the bold line inFig. 2 . - The cooling
oil 40 accumulated in an oil sump of anoil pan 15 is suctioned up through anintake port 30 by the rotaryvolumetric change pump 20, and the coolingoil 40 is pressure-fed to the coolingsubject device 17, such as the electric motor and the generator, through adischarge port 32 via anoil cooler 16. Theoil cooler 16 radiates heat of theoil 40 passing through. Then, theoil 40 which has cooled the coolingsubject device 17 is configured to return to theoil pan 15. - The rotary
volumetric change pump 20 is operated when a movement of themotor 12 is transmitted to theinner rotor 21, and the operation of themotor 12 is controlled by an electricoil pump controller 13. Ahost controller 14 sends a control signal to this electricoil pump controller 13. - When the
electric oil pump 11 is shut down, negative pressure is generated on theintake side 31 of the pump chamber in the rotaryvolumetric change pump 20. As described above, when the negative pressure increases, there is a possibility that air will enter the pump chamber. Particularly, it is known that when the viscosity coefficient of oil is high (for example, when the kinematic viscosity coefficient of oil is equal to or higher than approximately 1,000 mm2/s), since the oil is unlikely to be taken in, the negative pressure is likely to increase, thereby easily resulting in such a phenomenon. - Therefore, in the present invention, before the
electric oil pump 11 is shut down, the rotaryvolumetric change pump 20 is caused to rotate reversely by a predetermined angle so that the negative pressure is reduced or eliminated, thereby preventing air from entering the pump chamber. The motor 1 2 is controlled by the electricoil pump controller 13. A step of controlling themotor 12 carried out by the electricoil pump controller 13 will be described below using the drawings.Fig. 3 is a flow chart of control over themotor 12 conducted by the electricoil pump controller 13. - First, in Step S10 at the start, work is performed to turn on power, for example, an engine of a vehicle is started.
- Next, in Step S11, the electric
oil pump controller 13 receives a motor control signal. Then, in Step S12, it is determined whether or not the received control signal has changed. - In Step S12, when the control signal has not changed, the state is retained as it is, and the electric
oil pump controller 13 waits for reception of a control signal again. When the control signal has changed in Step S12, the process proceeds to Step S13, and it is determined whether or not the control signal is for operation or not. - In Step S13, when it is determined that the control signal is for operation, the process proceeds to Step S14, and the
motor 12 is caused to rotate normally. In Step S13, when it is determined that the control signal is not for operation, that is, in a case of a control signal for shutdown, the process proceeds to Step S15, and themotor 12 is caused to temporarily stop. Furthermore, the process proceeds to Step S16, and themotor 12 is caused to rotate reversely by a certain amount of rotation, thereby eliminating the negative pressure inside the pump chamber. Lastly, the process proceeds to Step S17, and themotor 12 is completely shut down. Naturally, the angle of the reverse rotation required to eliminate the negative pressure is determined depending on various factors such as the viscosity coefficient of oil and the shapes of rotors. Therefore, the angle varies case by case. However, in order to suppress generation of excessive negative pressure, it is considered that a sufficient effect can be obtained when theinner rotor 21 is caused to rotate reversely by 360 degrees. - In devices in the related art, when a control signal for a shutdown is received, it is usual that a motor is instantly shut down. However, as described above, the present invention is characterized in that after it is determined that a control signal is not for operation any longer, a step is performed at all times, in which the motor is caused to temporarily stop, the motor is caused to rotate reversely, and the motor is then completely shut down. If it is intended to determine whether or not the motor is to be caused to rotate reversely in accordance with the magnitude of negative pressure inside the pump chamber, the oil pressure has to be measured, so that there is a need to separately provide a device therefor. However, in the present invention, the motor is caused to rotate reversely at all times, and the angle of the reverse rotation is set in advance within a range in which a sufficient effect can be obtained and the circulation of oil is not affected. Accordingly, even though no extra device is provided, it is possible to achieve a sufficient effect.
- In this manner, if air can be prevented from entering the pump chamber by reducing or eliminating the negative pressure, when the pump is restarted, the pump chamber is in a state of being filled with oil. Therefore, even before the oil temperature sufficiently rises and the kinematic viscosity coefficient of the oil is lowered, it is possible to achieve an effect that the oil sufficiently circulates and the oil can be smoothly discharged.
- The configuration of the present invention is not limited to only oil pumps used for cooling a device and can also be widely utilized in devices in which fluid having a high viscosity coefficient is supplied and circulates.
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- 10 Oil supply device
- 11 Electric oil pump
- 12 Motor
- 13 Electric oil pump controller
- 14 Host controller
- 20 Rotary volumetric change pump
- 21 Inner rotor
- 22 Outer rotor
- 30 Intake port
- 31 Intake side of pump chamber
- 32 Discharge port
- 33 Discharge side of pump chamber
- 40 Oil
Claims (6)
- An oil supply device (10) comprising:an electric oil pump (11) in which a rotary volumetric change pump (20) provided with an inner rotor (21) and an outer rotor (22) is operated by a motor (12), andcharacterized in further comprising:
an electric oil pump (11) controller which controls the motor (12) such that when the electric oil pump (11) is to be shut down, the rotary volumetric change pump (20) is caused to temporarily stop and to rotate by a predetermined angle in a direction opposite to a rotation direction during oil supply, and the electric oil pump (11) is then shut down, so that the negative pressure on an intake side (31) of a pump chamber in the rotary volumetric change pump (20) is reduced or eliminated, thereby preventing air from entering the pump chamber. - The oil supply device (10) according to claim 1,
wherein the predetermined angle, by which the rotary volumetric change pump (20) is caused to rotate in the direction opposite to the rotation direction during oil supply, is 360 degrees with respect to the inner rotor (21). - The oil supply device (10) according to claim 1 or 2,
wherein a kinematic viscosity coefficient of oil to be supplied using the rotary volumetric change pump (20) is equal to or higher than 1,000 mm2/s. - A method of controlling an electric oil pump (11), characterized in comprising:
controlling a motor (12) such that when the electric oil pump (11), in which a rotary volumetric change pump (20) provided with an inner rotor (21) and an outer rotor (22) is operated by the motor (12), is to be shut down, the rotary volumetric change pump (20) is caused to temporarily stop and to rotate by a predetermined angle in a direction opposite to a rotation direction during oil supply so that the negative pressure on an intake side (31) of a pump chamber in the rotary volumetric change pump (20) is reduced or eliminated, thereby preventing air from entering the pump chamber, and the electric oil pump (11) is then stopped. - The method of controlling an electric oil pump (11) according to claim 4,
wherein the predetermined angle, by which the rotary volumetric change pump (20) is caused to rotate in the direction opposite to the rotation direction during oil supply, is 360 degrees with respect to the inner rotor (21). - The method of controlling an electric oil pump (11) according to claim 4 or 5,
wherein a kinematic viscosity coefficient of oil to be supplied using the rotary volumetric change pump (20) is equal to or higher than 1,000 mm2/s.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015105767A JP6570878B2 (en) | 2015-05-25 | 2015-05-25 | Oil supply device and electric oil pump control method |
PCT/JP2016/064163 WO2016190121A1 (en) | 2015-05-25 | 2016-05-12 | Oil supply device and method of controlling electric oil pump |
Publications (3)
Publication Number | Publication Date |
---|---|
EP3306095A1 EP3306095A1 (en) | 2018-04-11 |
EP3306095A4 EP3306095A4 (en) | 2019-01-09 |
EP3306095B1 true EP3306095B1 (en) | 2020-04-22 |
Family
ID=57394201
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16799829.3A Active EP3306095B1 (en) | 2015-05-25 | 2016-05-12 | Oil supply device and method of controlling electric oil pump |
Country Status (5)
Country | Link |
---|---|
US (1) | US20180135624A1 (en) |
EP (1) | EP3306095B1 (en) |
JP (1) | JP6570878B2 (en) |
CN (1) | CN107614877B (en) |
WO (1) | WO2016190121A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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CN112780428B (en) * | 2019-11-05 | 2023-09-29 | 纬湃汽车电子(芜湖)有限公司 | Oil pump locked rotor diagnosis and repair method, oil pump controller and oil supply system |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB282707A (en) * | 1926-12-29 | 1928-07-26 | James Butler Tuthill | Improvements in rotary pumps |
JPH0429774A (en) * | 1990-05-28 | 1992-01-31 | Takahiro Hoshino | Pump apparatus for emitting viscous solution |
JP3178093B2 (en) * | 1992-07-10 | 2001-06-18 | 松下電器産業株式会社 | Water heater transmitter / receiver |
JPH0630482U (en) * | 1992-09-21 | 1994-04-22 | 株式会社大盛鉄工所 | Oil pump |
JP2845174B2 (en) * | 1995-08-21 | 1999-01-13 | 大同機械製造株式会社 | Adduction gear pump |
US5711408A (en) * | 1996-05-09 | 1998-01-27 | Dana Corporation | Reversible gerotor pump |
JPH1193859A (en) * | 1997-09-18 | 1999-04-06 | Matsushita Electric Ind Co Ltd | Pump driving device |
JP3415417B2 (en) * | 1997-11-25 | 2003-06-09 | 株式会社東芝 | Motor control device |
US6530750B2 (en) * | 2000-03-21 | 2003-03-11 | Hy-Flex Corp. | Control for progressive cavity pump |
JP2004353624A (en) * | 2003-05-30 | 2004-12-16 | Aisin Seiki Co Ltd | Control method and device of motor-driven liquid pump |
JP2006258076A (en) * | 2005-03-18 | 2006-09-28 | Aisin Seiki Co Ltd | Electric liquid pump, its control method and control device |
JP2007291962A (en) * | 2006-04-25 | 2007-11-08 | Komatsu Ltd | Fluid pump |
CN201057143Y (en) * | 2007-06-18 | 2008-05-07 | 昆明理工大学 | Engine oil pump for single and dual-cylinder horizontal diesel engine |
-
2015
- 2015-05-25 JP JP2015105767A patent/JP6570878B2/en active Active
-
2016
- 2016-05-12 WO PCT/JP2016/064163 patent/WO2016190121A1/en active Application Filing
- 2016-05-12 CN CN201680029606.5A patent/CN107614877B/en active Active
- 2016-05-12 US US15/576,708 patent/US20180135624A1/en not_active Abandoned
- 2016-05-12 EP EP16799829.3A patent/EP3306095B1/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
WO2016190121A1 (en) | 2016-12-01 |
US20180135624A1 (en) | 2018-05-17 |
CN107614877A (en) | 2018-01-19 |
JP2016217316A (en) | 2016-12-22 |
EP3306095A4 (en) | 2019-01-09 |
JP6570878B2 (en) | 2019-09-04 |
EP3306095A1 (en) | 2018-04-11 |
CN107614877B (en) | 2019-10-15 |
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