Source: https://patents.google.com/patent/JP4586542B2/en
Timestamp: 2020-04-07 08:44:34
Document Index: 150531120

Matched Legal Cases: ['art 2', 'art 30', 'art 30', 'art 7', 'art 6', 'art 2', 'art 30', 'art 2', 'art 30', 'art 5', 'art 2', 'art 410', 'art 2', 'art 410', 'art 2', 'art 2', 'art 3', 'art 410', 'art 410', 'art 410', 'art 2', 'art 2', 'art 306', 'art, 3', 'art, 6', 'art, 8', 'art, 32']

JP4586542B2 - Rotating electric machine - Google Patents
JP4586542B2
JP4586542B2 JP2005009219A JP2005009219A JP4586542B2 JP 4586542 B2 JP4586542 B2 JP 4586542B2 JP 2005009219 A JP2005009219 A JP 2005009219A JP 2005009219 A JP2005009219 A JP 2005009219A JP 4586542 B2 JP4586542 B2 JP 4586542B2
JP2005009219A
JP2006197772A (en
2005-01-17 Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
2005-01-17 Priority to JP2005009219A priority Critical patent/JP4586542B2/en
2006-07-27 Publication of JP2006197772A publication Critical patent/JP2006197772A/en
2010-11-24 Publication of JP4586542B2 publication Critical patent/JP4586542B2/en
2025-01-17 Anticipated expiration legal-status Critical
The present invention relates to a rotating electrical machine, and more particularly to a rotating electrical machine having a cooling flow path for flowing a cooling fluid.
To operate a rotating electrical machine (motor, generator, or motor / generator) under severe load conditions or to reduce the size of the rotating electrical machine, it is necessary to quickly dissipate the heat generated in the coil and stator core. There is. This is because when the temperature of the stator rises, the enamel coating of the enameled wire of the coil and the insulating paper that insulates the coil from the stator core will burn out.
In recent years, vehicles such as electric vehicles, hybrid vehicles, and fuel cell vehicles that use a rotating electrical machine as a drive source together with or in place of an engine have appeared. A rotating electrical machine mounted on such a vehicle is particularly demanded for operation under such a severe load condition and miniaturization.
In the prior art, there is a technique in which a coolant is directly applied to the coil winding portion in order to reduce the coil temperature and prevent the enamel coating and the insulating paper from being burned out. For example, this is a technique in which a cooling liquid supply port is provided in an upper part of a case of a rotating electrical machine, and the cooling liquid is sprayed from the cooling liquid supply port to the coil to cool the coil.
However, if the cooling liquid is supplied to the coil and then left to drop by gravity, the actual area covered with the cooling liquid is limited to about 30 to 60% of the outer surface of the coil, and the rest The coil surface portion of the coil is not cooled and is still air-cooled. Therefore, although the coil temperature is reduced as compared with the case where the entire surface area of the coil is air-cooled, the coil temperature is increased in a region (high rotation region or large torque region) where the operating conditions are more severe.
JP 2002-272041 A (Patent Document 1), JP 4-364343 A (Patent Document 2), JP 2003-289650 A (Patent Document 3), JP 2003-224945 A (Patent Document 4). ) Discloses a structure in which a coil-type winding end face of a stator of a rotating electrical machine is provided with a closed cooling channel. With such a configuration, the cooling effect on the coil is improved rather than simply injecting the coolant into the coil and leaving the flow determined by gravity.
JP 2002-272041 A JP-A-4-364343 JP 2003-289650 A JP 2003-224945 A
However, in the configuration disclosed in the prior documents such as the above-mentioned Japanese Patent Application Laid-Open No. 2002-272041 (Patent Document 1), the coolant is supplied from the upper part of the rotating electrical machine and discharged from the lower part. In such a configuration, a portion cooling liquid does not contact occurs in places in supply amount unless coil end face portion sufficient coolant, there is a problem that cooling performance is not sufficient.
An object of the present invention is to provide a rotating electrical machine with improved cooling capacity.
In summary, the present invention is a rotating electrical machine, wherein a stator core, a coil wound around the stator core, and at least a part of a portion of the coil wound around the stator core are immersed in a cooling fluid. And a flow rate controller configured to control a supply amount or a discharge amount of the fluid so that the inside of the cooling channel is appropriately filled with the fluid.
Preferably, the cooling flow path is provided with a fluid supply port on the upper side of the stator core and a fluid discharge port on the lower side of the stator core. The flow rate control unit includes a flow rate control valve attached to the fluid discharge port.
Preferably, a detection means for detecting the state of the rotating electrical machine is provided. The flow rate controller changes the coil immersion level of the fluid filled in the cooling flow path according to the output of the detection means.
According to another aspect of the present invention, in the rotating electric machine, a stator core, a coil wound around the stator core, and at least a part of a portion of the coil wound around the stator core are immersed in a cooling fluid. And a cooling channel arranged in this manner. In the cooling channel, a fluid supply port is provided on the lower side of the stator core, and a fluid discharge port is provided on the upper side of the stator core.
More preferably, the rotating electrical machine further includes a check valve attached to the fluid supply port.
Preferably, the fluid discharge port is provided at a position where the fluid discharged from the fluid discharge port is supplied to a gap between the case housing the stator core and the stator core.
Preferably, the rotating electrical machine further includes a resin mold portion that fixes the coil to the stator.
According to the present invention, since the portion where the coil is in contact with the cooling fluid is expanded by adopting the closed flow path, the heat transfer area between the cooling oil and the coil is increased, and the thermal resistance between the coil and the cooling oil is greatly increased. And more efficient cooling of the motor becomes possible.
Further, since the heat radiation path directly radiates heat from the coil to the cooling oil, the thermal resistance between the coil and the cooling oil can be greatly reduced, and the motor can be efficiently cooled.
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Note that the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.
In the first embodiment, in the motor in which the coil portion of the stator is molded, the motor can be operated under severe load conditions by directly liquid cooling the coil, and the motor can be reduced in size. Propose structure.
FIG. 1 is a front view of a stator 1 used in Embodiment 1 of the present invention.
2 is a cross-sectional view taken along the line II-II in FIG.
1 and 2, the stator 1 has a cylindrical shape capable of accommodating a rotor therein, and includes covers 60 and 79 on both side surfaces. The cover 60 is fixed to the mold resin portion 2 of the stator by bolts 61 to 67 disposed on the outer peripheral side of the stator and bolts 70 to 77 disposed on the inner peripheral side.
FIG. 3 is a view as seen from the III-III direction with the cover 60 removed in FIG.
Referring to FIGS. 2 and 3, stator 1 has a stator core 8, coils 11 to 22 wound around the core portion of stator core 8, and an annular shape that accommodates a rotor therein, and coil 11 And resin part 2 fixed to and supported on stator core 8 by resin molding.
In FIG. 3, the upper and lower cross sections and the cylindrical inner surface of the stator are visible. The heads of the stator cores 8A to 8E are visible on the cylindrical inner surface.
A groove portion 30 for guiding cooling oil, which is a fluid for cooling, to approach the coils 11 to 22 is provided on a surface perpendicular to the rotor and the rotation axis of the resin portion 2. The groove portion 30 is constituted by wall portions 3 and 5 protruding from the resin portion 2. In hybrid vehicles, ATF (Automatic Transmission Fluid) is often used as cooling oil.
From the inner wall of the groove part 30, a part of the coils 11 to 12 is exposed in a state where it is not buried in the resin part. The exposed part is a portion of the coil portion wound around the stator core 8 in the front direction of the rotation axis. Since the cooling oil directly contacts the coil, the heat of the coil is easily transmitted to the cooling oil, and the cooling efficiency is improved.
The groove part 30 has an annular shape, and a notch part 7 for allowing cooling oil to flow in and a notch part 6 for allowing cooling oil to flow out are provided on the wall part of the resin part 2 constituting the groove part 30. The cutout portion 7 is set larger than the cutout portion 6, whereby the cooling oil easily accumulates in the lower portion of the groove, so that the coil is easily immersed in the cooling oil, and the cooling efficiency is further improved.
After the stator core is set in the coil, the stator core is inserted into the mold and the resin part 2 is formed by injection molding. By this molding, the groove 30 serving as a cooling oil passage is integrally formed with the resin section having a concave cross-sectional shape.
The cooling oil is supplied from the notch 7 on the upper side in the gravitational direction, flows in the flow path formed by the annular groove 30 on the mold and the cover 60 while cooling the coils 11 to 22, and the lower cover in the gravitational direction. The gas is sequentially discharged from an orifice 78 which is a discharge port provided at a lower portion of the 60.
Inside the groove portion 30 formed by the mold, for example, cooling oil is applied as evenly as possible to the coils 11 to 22, and a protrusion for guiding the cooling oil appropriately at the time of molding in order to improve heat transfer from the coil to the cooling oil. The part may be provided inside the groove part 30.
In the configuration shown in FIGS. 1 and 2, an example is shown in which a part of the coil is exposed from the outer surface of the resin mold. However, the groove of the coil is provided in the resin mold without being exposed. If the cooling oil is guided to the vicinity, the coil cooling has a certain effect.
FIG. 4 is a view for explaining a configuration for supplying oil to a notch provided in the upper portion of the stator 1.
Referring to FIG. 4, rotating electrical machine 50 includes a stator 1, a rotor 32 disposed inside stator 1, a case 34 that houses stator 1 and rotor 32, and a rotating shaft of rotor 32 that is fixed to case 34. Ball bearings 38 and 40 that rotatably support 42, and an oil pump 36 attached to the rotating shaft 42 and attached to the outside of the case 34. The stator 1 is fixed to the case 34 with bolts 53.
The case 34 is provided with an oil suction passage 46 for sucking oil from an oil sump 44 inside the case and an oil discharge passage 48 for supplying oil sent from the oil pump 36 to the stator 1 for cooling. Oil discharge ports 51 and 52 are provided at the end portion of the oil discharge passage 48, and cooling oil is supplied to the central portion of the notch portion 7 of the stator 1.
The cooling oil is first pumped up by an oil pump 36 from an oil reservoir 44 at the bottom of the case, and is supplied from an oil suction passage 46 provided in the case 34 to the notch 7 of the stator through the oil discharge passage 48 through the oil pump 36. The The supplied cooling oil returns to the oil sump 44 due to gravity drop after cooling the stator 1. An oil cooler may be inserted between the oil reservoir 44 and the oil pump 36.
Since the groove 30 is surrounded by the walls 3 and 5 and covered with the cover 60 as shown in FIGS. 2 and 3, the cooling oil is applied to most of the exposed portions of the coils 11 to 22, and the gravity oil It is guided to the orifice 78 in the lower direction. For this reason, the cooling oil does not flow into the air gap between the rotor 32 and the stator 1 in FIG.
When cooling oil enters the air gap between the stator 1 and the rotor 32, a power loss occurs due to shearing. Since the wall part 5 is provided, such power loss can be prevented.
FIG. 5 is a diagram for explaining another configuration for supplying oil.
FIG. 6 is a cross-sectional view taken along the VI-VI plane in FIG.
5 and 6 show a configuration in which the cooling oil attached to the outside of the case 34 is supplied instead of the oil pump 36 in the configuration of the rotating electrical machine 50 including the stator 1 and the rotor 32 shown in FIG.
An output gear 152 is fixed to the rotating shaft 42 of the rotor 32. The gear 150 is configured to have a larger diameter than the output gear 152, and they are meshed with each other outside the motor case 34. The lower part of the gear 150 is immersed in the lubricating oil stored in the first oil chamber 154.
The first oil chamber 154 is provided with a second oil chamber 158 divided by a partition wall 156, and the lubricating oil is stored in each of them. The second oil chamber 158 communicates with the oil sump 44 in FIG. Since the partition wall 156 includes a throttle oil passage (orifice) 160 at an intermediate portion in the height direction, the amount of the lubricating oil stored in the second oil chamber 158 is restricted while flowing in through the throttle oil passage 160. One oil chamber 154 is supplied.
An oil receiving plate 162 is disposed substantially horizontally above the output gear 152, and a pair of cooling oil supply ports 118 are provided in a space 166 between the oil receiving plate 162 and the gear box 164.
Therefore, as the rotary shaft 42 of the rotor 32 rotates, the large-diameter gear 150 meshed with the output gear 152 rotates around the rotary shaft 168 extending in the horizontal direction and is stored in the first oil chamber 154. The lubricating oil is scraped up by the large diameter gear 150.
Then, the lubricating oil is fed into the space 166 and supplied as cooling oil into the motor case 34 through the cooling oil supply port 118. That is, the rotating electrical machine cools itself by supplying the cooling oil in the first oil chamber 154 as the rotating shaft 42 rotates. The cooling oil supply port 118 corresponds to the oil discharge path 48 of FIG.
At this time, the lubricating oil stored in the first oil chamber 154 is scraped up by the large-diameter gear 150 immersed in the lower part thereof as the rotary shaft 42 rotates, and is supplied into the motor case 34. Is done. The amount of lubricating oil supplied from the second oil chamber 158 to the first oil chamber 154 is limited by the throttle oil passage 160 provided in the partition wall 156. Therefore, since the lubricating oil stored in the first oil chamber 154 is kept at a constant amount, the lubricating oil becomes excessive and the loss due to the stirring resistance of the large-diameter gear 150 immersed therein is suppressed, and the motor A sufficient amount of cooling oil can be supplied into the case 34 to stably cool the rotating electrical machine.
As described above, in the first embodiment, in the motor in which the stator is resin-molded, a part of the coil wound around the stator core is exposed from the outer surface of the mold as shown in FIG. A stator structure in which a flow path is formed in the mold resin portion so that the coil can be directly cooled by oil is adopted.
This flow path is formed by sealing a groove provided in the mold resin portion 2 with covers 60 and 79. Then, the cooling oil is supplied from the upper side in the gravity direction and discharged from the lower side in the gravity direction. An orifice 78 is provided in the cooling oil discharge port in order to immerse all portions of the coil exposed in the flow path sealed by the covers 60 and 79 with the cooling oil.
The characteristic configurations of the first embodiment will be listed.
(A) A part of a portion of the coil wound around the stator core is exposed from the outer surface of the mold resin portion 2.
(B) The notch portion 7 as a cooling oil supply port is provided on the upper side of the resin mold in the gravity direction in use. This notch may be provided in the covers 60 and 79 without being provided in the resin mold.
(C) The cover 60, 79 is provided with a cooling oil discharge port. The discharge port may be provided with a notch on the lower side in the gravity direction of the mold during molding.
(D) A groove for guiding the cooling oil is provided by forming the resin mold cross-sectional shape as a recess.
(E) A sealed flow path is formed by attaching the covers 60 and 79 to the mold resin portion 2. In addition, it is preferable to seal between the mold resin part 2 and the covers 60 and 79 with an O-ring or a gasket. When the cooling oil is supplied from the upper part in the gravity direction, the cooling oil is discharged from the lower port in the gravity direction while cooling the exposed portion of the coil.
(F) The discharge port is provided with an orifice 78 so that the coil end is completely immersed in the cooling oil.
In addition, a projecting member is provided on the inner portion of the flow path at the time of molding so that the cooling oil is evenly applied to the coil as much as possible in the flow path portion formed in (e) to increase the heat transfer area between the coil and the cooling oil. Also good.
Further, depending on the required level of cooling performance, the flow path may be formed so that the cooling oil flows near the coil without exposing the coil winding portion from the outer surface of the mold.
By adopting such a structure, since the heat radiation path is directly radiated from the coil to the cooling oil, the thermal resistance between the coil and the cooling oil can be greatly reduced, and the motor can be efficiently cooled. It becomes possible.
Also, by adopting a closed flow path and providing an orifice, the entire area of the exposed portion of the coil is in contact with the cooling oil, so the heat transfer area between the cooling oil and the coil becomes large, and the thermal resistance between the coil and the cooling oil is reduced. This greatly reduces the motor cooling efficiency.
Further, since the flow path has a sealed structure by the mold resin portion 2 and the covers 60 and 79, the cooling oil is difficult to enter the air gap between the stator 1 and the rotor 32, and the cooling oil is sheared by the rotor 32. Power loss can be prevented.
In the second embodiment, in the structure of the rotating electrical machine described in the first embodiment, the cooling oil supply amount, the flow path shape, and the orifice 78 provided in the cooling oil discharge port are set such that the cooling oil supply amount> the discharge amount. The cross-sectional area is set.
FIG. 7 is a diagram for explaining the flow of the cooling oil.
Referring to FIG. 7, the cooling oil is supplied from notch 7, and the cooling oil flows through the flow path as shown by the arrow in FIG. 7 and is discharged from orifice 78.
When the cooling oil supply amount is Qin, the immersion height is D1, the flow coefficient is C, the gravitational acceleration is G, the initial oil surface height is h0, and the sectional area of the orifice 78 is B, the following equation (1) Each value is determined so that the relationship is established.
Qin ≧ D1 · C · (G / 2h0) 1/2 · B (1)
That is, in order to completely fill the flow path space sealed by the mold resin portion 2 and the covers 60 and 79 with the cooling oil and immerse the entire coil in the cooling oil, Qin ≧ Qout may be satisfied. The cooling oil amount Qout discharged from the cooling oil discharge orifice 78 is expressed by the right side of the equation (1). Therefore, if each specification of the stator cooling structure is determined so as to satisfy the expression (1), the entire coil can be immersed in the cooling oil, and the cooling performance of the stator can be further improved.
Therefore, according to the second embodiment, even when the supply amount of the cooling oil is small, the entire coil surface area can be surely immersed in the cooling oil, and the coil temperature can be further reduced.
In the first embodiment and the second embodiment, the cooling capacity is improved by immersing the coil portion exposed from the resin mold in the cooling oil. However, when motor components such as enameled wires and insulating paper are heated to a high temperature in a state where they are immersed in cooling oil, their mechanical strength and insulation strength are reduced by hydrolysis due to a small amount of water in the cooling oil. .
Therefore, in order to improve the cooling performance, it is desirable to immerse the coil in the cooling oil as much as possible. However, since the oil resistance (hydrolysis resistance) of the enameled wire and insulating paper material must be improved, the material cost of these members Will be up.
In the third embodiment, in a motor that directly oil-cools a coil, oil resistance of components such as enameled wire and insulating paper is extremely improved by making the coil immersion level variable according to the coil temperature. We propose a motor that can be operated under severe load conditions and can be downsized.
FIG. 8 is a block diagram illustrating a configuration of the rotating electrical machine 200 according to the third embodiment.
Referring to FIG. 8, rotating electric machine 200 includes a coil immersion level variable stator 202, a cooling oil discharge flow rate controller 204, an oil pump 36, and an oil sump 44.
Coil immersed level variable stator 20 2 includes a coil sealed structure stator 1 shown in the first embodiment, the coil temperature detecting unit 206 for detecting the temperature of the stator coil of the coil sealed structure stator 1, a coil closed structure stator 1 Oil And a solenoid valve 208 attached to the discharge port.
The coil temperature detection unit 206 is fixed by embedding a temperature sensor in the vicinity of the coil shown in FIG. 3 having a coil sealing structure or between the coils and integrally molding the resin with a resin mold. The solenoid valve 208 is assembled to the cooling oil discharge port in place of the orifice 78 of the cover 60 in FIG. 1, and the flow path is opened when the solenoid valve 208 is not energized, and the flow path is closed when energized. (Normally open).
When cooling oil is supplied from the upper part in the direction of gravity, the oil is discharged from the port in the lower part of the direction of gravity while cooling the portion of the coil exposed to the flow path. An electromagnetic valve 208 for controlling the cooling oil discharge flow rate is assembled to the discharge port, and the cooling oil discharge flow rate controller 204 is connected to the electromagnetic valve 208 according to the temperature sensor signal TCOIL from the coil temperature detection unit 206. On the other hand, an on / off signal is issued. By adjusting this on / off signal, the coil immersion level of the cooling oil can be made variable.
In FIG. 8, the cooling oil is shown to be supplied by the oil pump 36, but as described in FIGS. 5 and 6, the cooling oil stored in the lower portion of the motor housing is pumped up by the gear, and the case A configuration may be adopted in which the liquid is supplied by gravity drop through a flow path provided in the.
FIG. 9 is a flowchart for explaining the control executed by the cooling oil discharge flow rate controller 204 of FIG.
Referring to FIG. 9, first, in step S1, the controller 204 takes in the temperature sensor signal TCOIL from the coil temperature detection unit 206, and measures the coil temperature T1. Subsequently, in step S2, the controller 204 determines whether or not the coil temperature T1 is equal to or higher than the threshold temperature T *.
The threshold value T * is a value determined from the heat-resistant temperature of the motor component and is obtained by the following equation (2).
T * = T0−α (2)
Here, T0 is a heat resistant temperature of the motor component (enameled wire, insulating paper), and α is a margin value.
If the coil temperature T1 ≧ T * in step S2, the process proceeds to step S3. On the other hand, if T1 ≧ T * does not hold, the process returns to step S1 again.
In step S <b> 3, the controller 204 sends an ON command to the electromagnetic valve 208. As a result, the solenoid valve 208 is closed, and the coil immersion level starts to increase. In step S4, the timer in the controller 204 starts. Thereby, time measurement is started.
In step S5, it is determined whether or not the measurement time t is equal to or greater than the measurement time threshold t1.
The threshold value t1 of the measurement time is obtained from the cooling oil supply amount Q and the sealed portion volume V by the equation (3).
t1 = V / Q (3)
While the measurement time does not reach the threshold value t1, time is waited in step S5, and when the measurement time is equal to or greater than t1, the process proceeds to step S6.
In step S6, the controller 204 again takes in the temperature sensor signal TCOIL from the coil temperature detector 206 and measures the coil temperature T2.
When the measurement in step S6 ends, the process proceeds to step S7, and it is determined whether or not the coil temperature T2 is less than a threshold value T ** defined by the following equation (4).
T ** = T * −β (4)
Here, T * is the threshold value already obtained by Expression (2), and β is a margin value.
In step S7, if the coil temperature T2 is equal to or higher than the threshold temperature T **, the process proceeds to step S3, where the solenoid valve is turned on and closed to increase the coil immersion level.
On the other hand, if the coil temperature is lower than the threshold temperature T ** in step S7, the process proceeds to step S8. In step S8, the solenoid valve is turned off to open it, and the coil immersion level is lowered. When step S8 ends, the process proceeds to step S9, and the one-cycle process ends.
For example, if T0 = 160 ° C., α = 20 ° C., β = 40 ° C., the solenoid valve for controlling the cooling oil discharge flow rate is turned on when the coil temperature is 140 ° C. or higher, and cooling can be performed in a completely immersed state. it can. And if coil temperature falls to 120 degrees C or less, the solenoid valve for cooling oil outflow flow rate control will be in an OFF state, and it will return to the original cooling state.
The coil immersion level is adjusted by performing the processing shown in FIG. 9 every predetermined time. In the third embodiment, an electromagnetic valve 208 is attached to the stator 1 having the cooling structure of the first embodiment. When the coil temperature T1 measured by the coil temperature detection unit 206 exceeds the threshold value T *, the electromagnetic valve is closed and all the sealed structural parts are immersed in the cooling oil. When the coil temperature is equal to or lower than the threshold temperature T **, the solenoid valve is in an open state, and the cooling oil only flows by gravity drop at the coil end, and in this case, the cooling oil does not accumulate.
As described above, the rotating electrical machine described in the third embodiment can change the cooling performance because the immersed state of the exposed coil portion can be changed by the coil temperature. And, only when the coil temperature is high, it is completely immersed, and otherwise it is cooled by gravity drop of the cooling oil, thereby shortening the time that the components such as enameled wire and insulating paper are exposed to the cooling oil. I can leave. Thereby, the fall of a machine and insulation strength can be suppressed few. Further, the oil resistance level of enameled wire, insulating paper, etc. can be lowered, and the cost of the constituent members can be reduced.
In the fourth embodiment, the control of the solenoid valve performed by the controller 204 in the third embodiment is different.
FIG. 10 is a flowchart for illustrating control performed by controller 204 in the fourth embodiment.
Referring to FIG. 10, when the process is started, first, in step S11, controller 204 takes in temperature sensor signal TCOIL output from coil temperature detection unit 206 and measures coil temperature Ti. Subsequently, the process proceeds to step S12, and it is determined whether or not the coil temperature Ti is equal to or higher than the coil temperature threshold value T *. Since coil temperature threshold value T * has been described in the third embodiment using equation (2), description thereof will not be repeated. If Ti ≧ T * is satisfied in step S12, the process proceeds to step S13. On the other hand, if Ti ≧ T * does not hold, the process proceeds to step S21.
In step S21, the controller 204 starts a built-in timer. Thereby, measurement of time t is started.
Subsequently, in step S22, it is determined whether or not the measurement time t exceeds the time threshold value t2, and the process waits until t ≧ t2.
The threshold value t2 of the measurement time used in step S22 is obtained from the cooling oil supply amount Q and the sealed portion volume V by the equation (5).
t2 = V / Q (5)
When the time t ≧ t2 is established in step S22, the process proceeds to step S23, and the coil temperature Ti + 1 is obtained by the next measurement of the coil temperature Ti.
Subsequently, in step S24, ΔT which is a difference between the coil temperature Ti measured last time and the coil temperature Ti + 1 measured in step S23 is calculated. Subsequently, in step S25, it is determined whether or not the coil temperature change amount ΔT exceeds a predetermined threshold value ΔTth.
If ΔT ≧ ΔTth is not satisfied in step S25, the process returns to step S11. On the other hand, if ΔT ≧ ΔTth is established in step S25, the process proceeds to step S13.
In steps S13 to S19, processing similar to that in steps S3 to S9 described in FIG. 9 is performed. Since these are described in FIG. 9, the description will not be repeated.
As described above, in the fourth embodiment, when the coil temperature change amount ΔT measured by the coil temperature detection unit 206 exceeds a certain threshold value ΔTth by the processing shown in steps S21 to S24, the process proceeds to step S13. In addition, all the flow paths having a sealed structure are immersed in the cooling oil. This improves the cooling capacity. After that, when the coil temperature is equal to or lower than the threshold value T **, the solenoid valve is opened in step S18, and the cooling oil only flows due to gravity drop.
In this way, in addition to the case where the temperature exceeds a predetermined value, the coil can be quickly immersed in the cooling oil even when the temperature change is large, and the cooling performance can be improved. Can be prevented. For example, the case where such a temperature change is large is a case where the amount of current supplied to the coil is large, such as when the vehicle climbs a steep slope or when sudden acceleration is performed during overtaking.
In the fifth embodiment, the control performed by the controller 204 shown in FIG. 8 of the third embodiment is different from the third embodiment.
FIG. 11 is a flowchart for illustrating control performed by controller 204 in the fifth embodiment.
Referring to FIG. 11, each process of steps S31 to S39 corresponds to the process of steps S1 to S9 of FIG.
The process of FIG. 9 differs from the process of FIG. 11 in that the process of steps S41 to S46 is executed when the coil temperature T2 <T ** is not satisfied in step S37. Therefore, since each process of steps S31 to S39 has been described with respect to corresponding steps S1 to S9 using FIG. 9, description thereof will not be repeated.
In FIG. 11, when the coil temperature T2 <T ** is not satisfied in step S37, the process proceeds to step S41. In step S41, it is determined whether or not a coil temperature T2 ≧ TLIM is satisfied. Here, TLIM is a threshold value of the coil temperature and is obtained by the equation (6).
TLIM = T0−γ (6)
Here, T0 is a heat resistant temperature of the motor component (enameled wire, insulating paper), and γ is a predetermined margin value.
If T2 ≧ TLIM is not satisfied in step S41, the process returns to step S33. On the other hand, if T2 ≧ TLIM is established in step S41, the process proceeds to step S42. In step S42, the controller 204 in FIG. 8 starts output restriction control for the stator 1.
Subsequently, in step S43, the controller 204 reduces the current limit command value ICOIL to the motor. The current limit command value ICOIL is a limit value indicating the maximum current at that time that can be passed through the motor coil. Subsequently, in step S44, the controller 204 takes in the temperature sensor signal TCOIL from the coil temperature detector 206 and measures the coil temperature T3.
Subsequently, in step S45, the coil temperature T3 is compared with the threshold value TLIM. If T3 <TLIM does not hold in step S45, the process returns to step S43 to further reduce the current limit command value ICOIL to the motor.
On the other hand, if T3 <TLIM is established in step S45, the process proceeds to step S46, and the output restriction control is terminated. When the process of step S46 ends, the process proceeds to step S36, and the coil temperature T2 is measured.
About each process of step S31-S39, since step S1-S9 which respectively respond | corresponds using FIG. 9, description is not repeated.
As described above, in the fifth embodiment, when the coil temperature exceeds the threshold value T * determined from the heat-resistant temperature of the motor component, the solenoid valve is closed and all the sealing structure parts are made of cooling oil. It will be in the state immersed. Further, when the coil temperature exceeds the threshold value TLIM in that state, the controller 204 reduces the energization amount to the stator coil and prevents burning so that the coil temperature does not rise.
For example, if T0 = 160 ° C., α = 20 ° C., β = 40 ° C., and γ = 5 ° C., the coil temperature is 140 ° C. or higher and the solenoid valve 208 in FIG. Cooling is performed in the state where And if coil temperature falls to 120 degrees C or less, the solenoid valve 208 will be in the open state, and it will return to the original cooling state. On the other hand, when the coil temperature becomes 155 ° C. or higher, the controller 204 starts motor output restriction control for restricting the current flowing in the coil of the stator 1 to reduce the heat generation itself.
In this manner, in the fifth embodiment, the coil immersion level can be variably controlled, and the cooling capacity can be changed according to the state of the coil. Further, when the cooling capacity is insufficient even with the improved cooling performance due to the state where the coils are all immersed in the cooling oil, the motor constituent members can be completely prevented from being burned by limiting the motor output.
In the third to fifth embodiments, a coil temperature sensor is provided near the stator coil to detect the coil temperature. However, there is a slight time delay due to heat transfer in the resin and the reaction speed of the temperature sensor until the temperature is detected by the temperature sensor when the current is passed through the coil and the temperature of the coil rises. Exists. When the temperature rise of the coil is known in advance, it is desirable to increase the coil cooling capacity as soon as possible.
FIG. 12 is a block diagram illustrating a configuration of the rotating electrical machine 300 according to the sixth embodiment.
Referring to FIG. 12, rotating electric machine 300 includes a vehicle state measurement sensor 304, a coil temperature estimation unit 306, a cooling oil discharge flow rate control controller 204, and an oil pump that supplies cooling oil to coil immersion level variable stator 302. 36 and an oil sump 44 that receives the cooling oil discharged from the coil immersion level variable stator 302.
Vehicle state measurement sensor 304 includes a lubricant temperature detection unit 308, a shift position sensor 310, a throttle sensor 312, a vehicle speed sensor 314, and a brake switch 316. The coil immersion level variable stator 302 includes the stator 1 having the coil sealing structure described in the first embodiment, and an electromagnetic valve 208 assembled to the oil discharge port of the stator 1 instead of the orifice.
The vehicle state measurement sensor 304 outputs a signal STATE indicating the state of the vehicle detected by each built-in sensor. The coil temperature estimation unit 306 outputs a signal TCOIL indicating the temperature of the coil estimated by receiving the signal STATE. The controller 204 turns on / off the electromagnetic valve 208 in accordance with the coil temperature obtained by calculation. In addition, since the shape of the coil sealed structure stator 1 has been described with reference to FIGS. 1 to 3, description thereof will not be repeated.
FIG. 13 is a flowchart showing processing in which the coil temperature estimation unit 306 estimates the coil temperature.
The coil temperature estimation unit 306 is based on vehicle state signals such as a shift position sensor 310, a throttle sensor 312, a vehicle speed sensor 314, a brake switch 316, and a lubricant temperature detection unit 308 that are generally installed in commercial vehicles. Calculate coil temperature. The coil temperature estimation unit is actually written as a part of the program in the controller 204 or the motor control controller. However, in FIG. 12, the coil temperature estimation unit 306 is replaced with the controller 204 for easy understanding. It is shown as independent.
Referring to FIG. 13, first, in step S51, coil temperature estimating unit 306 calculates the amount of heat generated by the motor by the following equation (7).
Qin (T) = f (V (t), Trq (T)) (7)
Here, Qin is the amount of heat generated by the motor, V is the motor speed, and Trq is the motor torque. The motor generated heat amount Qin is stored in advance as a map as a function of the motor rotation speed V and the motor torque Trq, and the function f reads out the motor generated heat amount from this map.
Subsequently, in step S52, the heat radiation amount Qout from the coil is obtained according to the following equation (8).
Qout (t) = K2 (Tcoil (t) −α (t)) (8)
Here, Qout is the amount of heat released from the coil, K2 is the electric heat coefficient, α is the core temperature, and Tcoil is the coil temperature.
In step S53, the coil temperature increase amount is calculated by the following equation (9).
ΔT (t) = (Qin (t) −Qout (t)) / K1 (9)
Here, ΔT is the amount of coil temperature rise, Qout is the amount of heat released from the coil, and K1 is the heat capacity of the coil.
In step S54, the coil temperature Tcoil is calculated by the following equation (10).
Tcoil = Ti + ∫ΔT (t) (10)
Here, Ti is the initial temperature.
Finally, the process proceeds to step S55 and the coil temperature estimation process ends. The current coil temperature Tcoil can be obtained by repeatedly performing the processing of the flowchart shown in FIG.
FIG. 14 is a flowchart showing processing executed by the controller 204 of FIG.
Steps S61 to S75 in FIG. 14 correspond to steps S11 to S25 in the flowchart described in FIG. The flowchart of FIG. 14 differs from the flowchart of FIG. 10 in that the initial coil temperature Ti is calculated by the coil temperature estimation unit 306 instead of measuring the coil temperature in step S61, and similarly in step S73. The coil temperature Ti + 1 is calculated by the estimation unit 306. Regarding the processing of the other parts, the flowchart shown in FIG. 14 performs the same processing as each step of the flowchart of FIG. 10, and therefore description thereof will not be repeated.
As described above, the rotating electrical machine described in the sixth embodiment can change the cooling performance because the state of being immersed in the coil oil can be changed according to the coil temperature. And, if the coil is completely immersed in the cooling oil only when the coil temperature is high, and other than that, the cooling oil is cooled by gravity drop, so that components such as enameled wire and insulating paper are exposed to the cooling oil. Since the time is shortened, it is possible to suppress a decrease in machine and insulation strength. For this reason, since the required level of oil resistance of components such as enameled wire and insulating paper is lowered, the cost can be reduced.
In addition, since a temperature detection thermistor attached to the coil portion is not required, the cost can be reduced. Further, since there is no problem of a response delay of the temperature detection thermistor, it is possible to quickly increase the cooling capacity before the coil temperature rises too much.
In the first to sixth embodiments, the structure in which the cooling oil is supplied from the upper side in the gravity direction and discharged from the lower discharge port has been described. On the other hand, in the seventh embodiment, a description will be given of a stator that employs a structure in which cooling oil is supplied from the lower side in the gravity direction, and the entire coil is immersed in the cooling oil and discharged from the upper side in the gravity direction.
FIG. 15 is a front view of stator 400 used in the seventh embodiment.
16 is a cross-sectional view taken along the line XVI-XVI in FIG.
Referring to FIGS. 15 and 16, the stator 400 used in the seventh embodiment includes covers 406 and 408 instead of the covers 60 and 79 in the configuration of the stator 1 described with reference to FIGS. 1 to 3. Yes. The cover 406 is provided with a cooling oil supply port in a portion where the orifice 78 of the cover 60 is provided. A cooling oil discharge port 402 is provided at the upper part of the cover 406 in the gravity direction.
Further, a resin part 410 is used instead of the resin part 2. The resin part 410 is different from the resin part 2 in that the notch 7 of FIG. 3 provided in the resin part 2 is not provided and the wall part 3 is connected over the entire circumference. Note that the cover 408 has the same structure as the cover 406. Since the configuration of other stator 400 is the same as that of stator 1 described with reference to FIGS. 1 to 3, description thereof will not be repeated.
The stator 400 is configured such that a part of the coil winding portion is exposed from the outer surface of the resin mold. The cover 406 is provided with a cooling oil supply port at the bottom and a cooling oil discharge port at the top. Then, the part of the coil that is exposed by the mold resin portion 410 and the covers 406 and 408 is inside the oil flow path of the sealed structure. In addition, it is preferable to seal between the mold resin part 410 and the covers 406 and 408 with an O-ring or a gasket.
When the cooling oil is supplied from the lower part in the gravity direction, the oil flow path is completely immersed in the cooling oil, and the cooling oil is discharged from the discharge port 402 at the upper part in the gravity direction. A resin part 410 is formed by injection molding, and a check is made of a pole and a spring so that the coil can be kept immersed in the cooling oil even when the cooling oil supply pump is stopped at the cooling oil supply port. A check valve 404 that is a valve may be provided.
Further, depending on the required level of cooling performance, the exposed portion of the coil may not be in the exposed state as shown in FIG. 3, but the cooling oil may pass through the vicinity of the coil.
If the stator according to the seventh embodiment is employed, the exposed portion of the coil winding portion is in contact with the cooling oil, so that the heat transfer area between the cooling oil and the coil becomes large, and the coil-cooling The thermal resistance between the oils can be greatly reduced, and the motor can be efficiently cooled.
In addition, since the flow path through which the cooling oil flows by the resin mold and the cover has a sealed structure, the cooling oil can be prevented from entering the air gap between the stator and the rotor, thereby reducing the power loss that occurs. .
In addition, if the structure is such that oil flows from the lower supply port to the upper discharge port, the exposed part of the coil is completely cooled even when the amount of oil supply per hour is small or when the oil supply is often stopped It can be kept immersed in oil, and the cooling efficiency of the motor is further improved.
FIG. 17 is a front view of stator 500 used in the eighth embodiment.
18 is a cross-sectional view taken along the line XVIII-XVIII in FIG.
Referring to FIGS. 17 and 18, stator 500 includes covers 502 and 504 instead of covers 406 and 408 in the configuration of stator 400 described in FIGS. 15 and 16. Moreover, it replaces with the resin part 410 and contains the resin part 2 demonstrated in FIG. 2, FIG.
Regarding the configuration of the other parts, stator 400 described in the seventh embodiment and stator 500 of the eighth embodiment have the same configuration, and therefore description thereof will not be repeated.
The cover 502 is not provided with the cooling oil discharge port 402 provided in the cover 406 of FIG. Instead, a notch is provided in the upper part of the resin part 2 and overflow ports 506 and 508 for discharging cooling oil are formed.
FIG. 19 is a diagram for explaining the penetration of the cooling oil from the overflow port.
As shown in FIG. 19, the stator 400 is accommodated in a case, and a slight gap (about 70 μm) exists between the case upper portion 510 and the case lower portion 512 and the stator core. The cooling oil discharged from the overflow ports 506 and 508 penetrates into the gap between the case upper portion 510 and the stator core. Thereby, compared with the case where the space | gap is filled with air, the thermal resistance with respect to a case from a core is reduced.
FIG. 20 is a diagram for explaining the flow of oil discharged from the overflow port.
As shown in FIG. 20, the cooling oil discharged from the overflow ports 506 and 508 travels down the cylindrical surface of the resin mold outer diameter and falls downward due to gravity. In the stator 500 of the eighth embodiment, as shown in FIG. 3, a part of the coil winding portion is exposed from the outer surface of the mold. An oil flow path having a sealed structure is provided by providing a groove in the cross-sectional shape of the mold at the time of injection molding and covering the groove with a cover. It is preferable to seal between the mold and the cover with an O-ring or a gasket.
Then, a notch shape is provided on the upper side in the gravity direction of the mold by molding, and oil is discharged therefrom. In addition, you may provide this notch in a cover part.
Furthermore, by setting the outer diameter dimension of the cover> the outer diameter dimension of the resin mold, the overflowed cooling oil surely flows on the cylindrical surface of the outer diameter of the mold as shown in FIG.
When cooling oil is supplied from the lower part in the weight direction, the exposed part of the coil is completely immersed in the cooling oil, and the cooling oil overflows from the mold notch in the upper part in the gravity direction.
A part of the overflowing cooling oil fills the gap between the core and the case by capillary action. The rest falls while cooling the cylindrical surface of the outer diameter of the mold as shown in FIG. 17 and 18 so that the exposed portion of the coil winding portion is immersed in the cooling oil even when the cooling oil supply pump (not shown) is stopped in the cooling oil supply port. As shown, a check valve 404 composed of a ball and a spring is preferably attached.
Protrusion members are provided in the oil flow path when molding the resin mold so that the cooling oil is applied evenly to the coil as much as possible and the heat transfer area between the coil and the cooling oil can be increased. Also good.
Depending on the level of cooling performance required, it may be possible to provide a flow path so that oil passes through the vicinity of the coil without providing the exposed portion of the coil.
In the conventional configuration, heat radiation from the cylindrical surface of the outer diameter of the mold was transferred through air, so the heat dissipation effect could not be expected so much, but heat dissipation was not performed through air but by heat transfer through cooling oil. It is performed from the mold to the case. For this reason, the heat radiation effect is increased by about 10 times from the cylindrical surface of the outer diameter of the mold as compared with the case of air. Therefore, the motor can be efficiently cooled.
In addition, since the overflowed cooling oil is supplied between the core and the case, the thermal resistance between the core and the case is greatly reduced, so the coil generates heat and the amount of heat released from the core to the case increases. The coil temperature can be kept low. Compared to the case where air is used between the core and the case, the thermal resistance is reduced to 1/5, and a heat dissipation effect of about 5 times can be expected.
Furthermore, since the oil supply path to the gap between the core and the case becomes unnecessary, the case structure can be simplified (conventionally, an oil supply path is provided in the case to improve the heat transfer efficiency between the core and the case. Some are provided, but if the flow shown in FIG. 20 is made, the same effect can be expected even if the case structure is simplified.)
It is a front view of the stator 1 used for Embodiment 1 of this invention. It is sectional drawing in the II-II cross section of FIG. It is the figure which removed the cover 60 in FIG. 2, and was seen from the III-III direction. FIG. 3 is a diagram for explaining a configuration for supplying oil to a notch provided in an upper portion of a stator 1. It is a figure for demonstrating the other structure which supplies oil. It is sectional drawing in the VI-VI surface in FIG. It is a figure for demonstrating the flow of a cooling oil. FIG. 6 is a block diagram illustrating a configuration of a rotating electrical machine 200 according to a third embodiment. FIG. 9 is a flowchart for explaining control executed by a cooling oil discharge flow rate controller 204 in FIG. 8. FIG. 10 is a flowchart for illustrating control performed by controller 204 in the fourth embodiment. 10 is a flowchart for illustrating control performed by controller 204 in the fifth embodiment. It is a block diagram which shows the structure of the rotary electric machine 300 of Embodiment 6. FIG. It is the flowchart which showed the process which the coil temperature estimation part 306 estimates a coil temperature. 13 is a flowchart showing processing executed by a controller 204 in FIG. FIG. 10 is a front view of a stator 400 used in a seventh embodiment. It is sectional drawing in the XVI-XVI cross section of FIG. FIG. 10 is a front view of a stator 500 used in an eighth embodiment. It is sectional drawing in the XVIII-XVIII cross section of FIG. It is a figure for demonstrating permeation of the cooling oil from an overflow port. It is a figure for demonstrating the flow of the oil discharged | emitted from the overflow port.
1,400,500 Stator, 2,410 Mold resin part, 3,5 Wall part, 6,7 Notch part, 8,8A-8E Stator core, 11-22 coil, 30 groove part, 32 rotor, 34 Motor case, 36 Oil Pump, 38, 40 Ball bearing, 42 Rotating shaft, 46 Oil suction path, 48 Oil discharge path, 50 Rotating electric machine, 51, 52 Oil discharge port, 53, 61-67, 70-77 Bolt, 60, 79, 406, 408, 502, 504 Cover, 78 Orifice, 118 Cooling oil supply port, 150 gear, 152 Output gear, 154, 158 Oil chamber, 156 Partition, 160 Throttle oil passage, 162 Oil receiving plate, 164 Gear box, 166 Space, 168 Rotating shaft, 200,300 Rotating electric machine, 202, 302 Coil immersion level variable stator 204 controller 206 coil temperature detection unit 208 solenoid valve 304 vehicle state measurement sensor 306 coil temperature estimation unit 308 lubricant temperature detection unit 310 shift position sensor 312 throttle sensor 314 vehicle speed sensor 316 brake switch 402 Drain port, 404 check valve, 506,508 overflow port, 510 upper case, 512 lower case.
A coil wound around the stator core ;
A resin mold part for fixing the coil to the stator core ;
The resin mold portion exposes a coil end portion that is a part of the coil wound around the stator core, and molds the coil in a state of covering the remaining portion,
A rotating electrical machine , further comprising a cover that forms a cooling flow path disposed with the resin mold portion so that the coil end portion is immersed in a fluid for cooling .
The rotating electrical machine according to claim 1, further comprising a flow rate determining unit that controls a supply amount or a discharge amount of the fluid so that the cooling channel is appropriately filled with the fluid.
The rotating electrical machine according to claim 2, wherein the cooling flow path is provided with a fluid supply port on an upper side of the stator core and a fluid discharge port on a lower side of the stator core.
The flow rate determining unit is
The rotating electrical machine according to claim 3, comprising a flow control valve attached to the fluid discharge port.
The rotating electrical machine according to claim 3, wherein the flow rate determining unit is an orifice that defines a discharge amount of the fluid.
Comprising detection means for detecting the state of the rotating electrical machine,
The flow rate determining section, rotating electric machine according to the filled in the cooling flow passage wherein changing the coil dipping level of the fluid are, according to claim 2 or 3 in accordance with the output of said detecting means.
The rotating electrical machine according to claim 1, wherein the cooling flow path is provided with a fluid supply port on a lower side of the stator core and a fluid discharge port on an upper side of the stator core.
The rotating electrical machine according to claim 7 , further comprising a check valve attached to the fluid supply port.
The rotating electrical machine according to claim 7 or 8 , wherein the fluid discharge port is provided at a position where the fluid discharged from the fluid discharge port is supplied to a gap portion between the case housing the stator core and the stator core.
JP2005009219A 2005-01-17 2005-01-17 Rotating electric machine Expired - Fee Related JP4586542B2 (en)
JP2005009219A JP4586542B2 (en) 2005-01-17 2005-01-17 Rotating electric machine
CN2006800025074A CN101107767B (en) 2005-01-17 2006-01-10 Rotating electric machine
PCT/JP2006/300414 WO2006085429A1 (en) 2005-01-17 2006-01-10 Rotating electric machine
US11/793,401 US7919890B2 (en) 2005-01-17 2006-01-10 Rotating electric machine
EP06711695.4A EP1841046B1 (en) 2005-01-17 2006-01-10 Rotating electric machine
JP2006197772A JP2006197772A (en) 2006-07-27
JP4586542B2 true JP4586542B2 (en) 2010-11-24
ID=36793007
JP2005009219A Expired - Fee Related JP4586542B2 (en) 2005-01-17 2005-01-17 Rotating electric machine
US (1) US7919890B2 (en)
EP (1) EP1841046B1 (en)
JP (1) JP4586542B2 (en)
CN (1) CN101107767B (en)
WO (1) WO2006085429A1 (en)
JP4645200B2 (en) * 2005-01-17 2011-03-09 トヨタ自動車株式会社 Rotating electric machine stator and rotating electric machine
JP4225342B2 (en) 2006-10-04 2009-02-18 トヨタ自動車株式会社 In-wheel motor structure
JP4973167B2 (en) * 2006-12-11 2012-07-11 トヨタ自動車株式会社 Coil cooling device
JP2009081972A (en) * 2007-09-27 2009-04-16 Ihi Corp Cooling structure and cooling method of electric motor for large-scale industrial machine
JP4661849B2 (en) * 2007-09-27 2011-03-30 トヨタ自動車株式会社 Stator structure
JP4880559B2 (en) * 2007-09-28 2012-02-22 本田技研工業株式会社 Cooling structure in rotating electrical machines
JP4450050B2 (en) 2007-11-07 2010-04-14 トヨタ自動車株式会社 Motor cooling structure
JP5167868B2 (en) * 2008-03-03 2013-03-21 日産自動車株式会社 Electric motor
DK2109206T3 (en) 2008-04-10 2013-06-17 Siemens Ag Generator with a stator comprising cooling ducts as well as method for cooling a laminated stator by a generator
DE102008001622A1 (en) 2008-05-07 2009-11-12 Robert Bosch Gmbh Electric machine with spray and sump cooling
US7948125B2 (en) 2008-08-08 2011-05-24 GM Global Technology Operations LLC System and method for cooling an electric motor
JP4563475B2 (en) * 2008-08-11 2010-10-13 アイシン精機株式会社 Rotating electric machine
WO2010041673A1 (en) * 2008-10-09 2010-04-15 株式会社 明電舎 Rotating machine cooling structure
JP4535189B2 (en) * 2008-12-09 2010-09-01 トヨタ自動車株式会社 Rotating electric machine for vehicles
JP2010172129A (en) * 2009-01-23 2010-08-05 Nippon Steel Corp Method and apparatus for cooling rotating electric machine
JP2010187489A (en) * 2009-02-13 2010-08-26 Meidensha Corp Rotary electric machine
JP5075878B2 (en) * 2009-06-17 2012-11-21 本田技研工業株式会社 Electric motor
JP5075879B2 (en) * 2009-06-17 2012-11-21 本田技研工業株式会社 Electric motor
JP5386263B2 (en) * 2009-07-30 2014-01-15 日立オートモティブシステムズ株式会社 Rotating electric machine
JP2011130545A (en) * 2009-12-16 2011-06-30 Toyota Industries Corp Heat recovery device
JP5498773B2 (en) * 2009-12-24 2014-05-21 株式会社日本自動車部品総合研究所 Rotating electric machine
DE102010014649A1 (en) * 2010-04-12 2012-01-19 Liebherr-Werk Biberach Gmbh Self-propelled surface milling cutter with electric milling drum drive
CN102906969B (en) * 2010-04-23 2015-05-13 株式会社Ihi Rotating machine
EP2583372A2 (en) * 2010-06-21 2013-04-24 Nidec Motor Corporation Electric motor assemblies including stator and/or rotor cooling
US8432074B2 (en) 2010-08-23 2013-04-30 Remy Technologies, L.L.C. Disk style centrifugal pump
US8546983B2 (en) * 2010-10-14 2013-10-01 Remy Technologies, Llc Split drain system and method for an electric machine module
EP2639941B1 (en) 2010-11-12 2019-04-03 Kawasaki Jukogyo Kabushiki Kaisha Cooling structure for electric vehicle
KR101475369B1 (en) * 2010-12-22 2014-12-23 가부시키가이샤 아이에이치아이 Rotary machine
US8432075B2 (en) * 2011-01-14 2013-04-30 Remy Technologies, L.L.C. Electric machine having an integrated coolant level sensor
WO2012101813A1 (en) * 2011-01-28 2012-08-02 トヨタ自動車株式会社 Apparatus for cooling motor
JP5166566B2 (en) * 2011-03-31 2013-03-21 株式会社小松製作所 Insulator and stator and motor provided with the same
US8803380B2 (en) * 2011-06-03 2014-08-12 Remy Technologies, Llc Electric machine module cooling system and method
JP5652359B2 (en) * 2011-09-12 2015-01-14 株式会社豊田自動織機 Electric compressor
JP5492170B2 (en) * 2011-10-06 2014-05-14 株式会社神戸製鋼所 Power generator
JP5853583B2 (en) * 2011-10-24 2016-02-09 トヨタ自動車株式会社 Control device for permanent magnet rotating electrical machine
JP5985178B2 (en) * 2011-11-24 2016-09-06 Ntn株式会社 Motor control device
SE536235C2 (en) * 2011-12-06 2013-07-09 Bae Systems Haegglunds Ab Electric drive for motor vehicles
EP2605379B1 (en) * 2011-12-14 2015-04-29 GE Jenbacher GmbH & Co. OG System and Method for Cooling Dynamoelectric Machine
TWI455460B (en) * 2011-12-16 2014-10-01 Ind Tech Res Inst Electric machine with dual air/water cooling mechanism
US9197115B2 (en) * 2012-01-27 2015-11-24 Remy Technologies, Llc Electric machine cooling
JP2013158161A (en) * 2012-01-31 2013-08-15 Fuji Electric Co Ltd Rotary electric machine
US9755482B2 (en) * 2013-03-12 2017-09-05 Regal Beloit America, Inc. Electric machine with liquid cooling and method of assembling
JP6105387B2 (en) * 2013-05-22 2017-03-29 株式会社日本自動車部品総合研究所 Rotating electric machine
KR101509928B1 (en) 2013-09-24 2015-04-07 현대자동차주식회사 Motor apparatus for vehicle and control method of the same
JP6385669B2 (en) * 2013-11-27 2018-09-05 日立建機株式会社 Rotating electric machine and electric vehicle equipped with the same
JP6221804B2 (en) * 2014-02-13 2017-11-01 トヨタ自動車株式会社 Rotating electric machine stator
JP6181592B2 (en) * 2014-04-11 2017-08-16 トヨタ自動車株式会社 Rotating electric machine cooling device
JP2015231275A (en) * 2014-06-04 2015-12-21 Ntn株式会社 In-wheel motor drive device
JP5847258B1 (en) * 2014-08-28 2016-01-20 三菱電機株式会社 Rotating electric machine
DE102014221667A1 (en) * 2014-10-24 2016-04-28 Zf Friedrichshafen Ag Hybrid drive arrangement of a motor vehicle
US9793782B2 (en) 2014-12-12 2017-10-17 Hamilton Sundstrand Corporation Electrical machine with reduced windage
JP2016171703A (en) * 2015-03-13 2016-09-23 川崎重工業株式会社 Electric type rotary machine
JP6350375B2 (en) * 2015-04-17 2018-07-04 株式会社デンソー Rotating electric machine
JP6500878B2 (en) * 2016-11-16 2019-04-17 トヨタ自動車株式会社 Cooling structure of rotating electric machine
DE102018214282A1 (en) * 2018-08-23 2020-02-27 Mahle International Gmbh Method for manufacturing an electrical machine
JPS60156860U (en) * 1984-03-26 1985-10-18
JPH05169985A (en) * 1991-12-25 1993-07-09 Aisin Aw Co Ltd Cooling control device for vehicle motor
JP2000197311A (en) * 1998-12-25 2000-07-14 Toyota Motor Corp Coil-cooling structure of a rotary electric machine
JP2004048877A (en) * 2002-07-10 2004-02-12 Nissan Motor Co Ltd Rotary electric machine
WO2004019468A1 (en) * 2002-08-21 2004-03-04 Toyota Jidosha Kabushiki Kaisha Vehicle motor
JP2004215353A (en) * 2002-12-27 2004-07-29 Toyota Motor Corp Rotary electric machine
JP2004257594A (en) * 2003-02-24 2004-09-16 Nisshin Steel Co Ltd Cooling device and cooling method
JP2004357458A (en) * 2003-05-30 2004-12-16 Nippon Soken Inc Dynamo electric motor cooling system for vehicle
US3084418A (en) * 1959-03-03 1963-04-09 Sperry Rand Corp Method of encapsulating electrical stators
JPS60156860A (en) 1984-01-26 1985-08-17 Showa Touen Kk Tile unit
JPS6416238A (en) * 1987-07-09 1989-01-19 Fanuc Ltd Method of cooling motor
JPS6430441A (en) * 1987-07-23 1989-02-01 Fanuc Ltd Internal cooling type motor with liquid
JPH01283042A (en) * 1988-05-07 1989-11-14 Daifuku Co Ltd Linear motor
JP2716286B2 (en) 1991-06-10 1998-02-18 ファナック株式会社 Cooling structure of the stator winding and a manufacturing method thereof in the motor
JPH0775271A (en) * 1993-08-31 1995-03-17 Matsushita Electric Ind Co Ltd Motor
JPH089595A (en) * 1994-06-21 1996-01-12 Fuji Electric Co Ltd Cooler for permanent magnet synchronizer
JPH0993869A (en) * 1995-09-28 1997-04-04 Mitsubishi Electric Corp Rotating machine having liquid-cooled structure
JP3262716B2 (en) * 1996-08-02 2002-03-04 山洋電気株式会社 Molded motor
DE69926316T2 (en) * 1998-08-12 2006-04-20 Hitachi, Ltd. Alternator for motor vehicles
JP3506020B2 (en) 1998-10-07 2004-03-15 三菱ふそうトラック・バス株式会社 Cooling structure of rotating electric machine
JP3877898B2 (en) * 1999-02-23 2007-02-07 三菱電機株式会社 AC generator for vehicles
JP3661529B2 (en) * 1999-11-17 2005-06-15 日産自動車株式会社 Motor cooling device
JP3946950B2 (en) * 2000-10-17 2007-07-18 三菱電機株式会社 AC generator for vehicles
JP3506126B2 (en) 2001-03-14 2004-03-15 日産自動車株式会社 Rotating electric machine
JP2003224945A (en) 2002-01-30 2003-08-08 Nissan Motor Co Ltd Cooling structure of stator in dynamo-electric machine
JP3896882B2 (en) 2002-03-28 2007-03-22 日産自動車株式会社 Rotating electric machine
JP2005269786A (en) * 2004-03-19 2005-09-29 Yaskawa Electric Corp Motor
2005-01-17 JP JP2005009219A patent/JP4586542B2/en not_active Expired - Fee Related
2006-01-10 US US11/793,401 patent/US7919890B2/en not_active Expired - Fee Related
2006-01-10 EP EP06711695.4A patent/EP1841046B1/en not_active Expired - Fee Related
2006-01-10 CN CN2006800025074A patent/CN101107767B/en not_active IP Right Cessation
2006-01-10 WO PCT/JP2006/300414 patent/WO2006085429A1/en active Application Filing
US7919890B2 (en) 2011-04-05
EP1841046A1 (en) 2007-10-03
US20070278869A1 (en) 2007-12-06
CN101107767A (en) 2008-01-16
CN101107767B (en) 2012-11-07
EP1841046A4 (en) 2015-05-20
EP1841046B1 (en) 2016-04-13
WO2006085429A1 (en) 2006-08-17
JP2006197772A (en) 2006-07-27
KR101076783B1 (en) 2011-10-26 Starter solenoid switch with improved arrangement of resistor
JP3423701B2 (en) 2003-07-07 Magnetorheological fluid clutch
US7654241B2 (en) 2010-02-02 Dual-chamber type oil pan and engine equipped with same
US8876501B2 (en) 2014-11-04 Electric pump unit
DE102005048859B4 (en) 2017-06-14 Blower clutch control method in the manner of an external control
KR20130093622A (en) 2013-08-22 Electric water pump with stator cooling
JP4563475B2 (en) 2010-10-13 Rotating electric machine
DE112012000617T5 (en) 2013-11-07 Mounting arrangement for a power control unit
DE112007000991B4 (en) 2010-10-21 Capacitor module
WO2011104909A1 (en) 2011-09-01 Rotary electric machine system
EP2737613B1 (en) 2017-02-01 Rotating electric machine and method for controlling the rotating electric machine
JP5261514B2 (en) 2013-08-14 Mounting structure of power control device
JP3775348B2 (en) 2006-05-17 Rotating electric machine
JP2009074517A (en) 2009-04-09 Drive circuit integral-type electric compressor
JP2004248402A (en) 2004-09-02 Driver for vehicle
JP4704137B2 (en) 2011-06-15 Electric motor cooling structure and construction machine vehicle equipped with the electric motor
FR2933821B1 (en) 2019-06-28 External rotor engine
CN102072169B (en) 2015-05-20 Electric water pump
KR101466779B1 (en) 2014-12-01 Power unit