JP2012244659A - Stator structure of rotary electric machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To efficiently cool a coil end of a stator of a rotary electric machine.SOLUTION: A refrigerant inlet port 2 and a refrigerant outlet port 8 are respectively provided at the vertically upper side and the vertically lower side of a refrigerant case 4 covering a coil end of a stator, and an opening 10 is provided at the same position as a rotary electric machine shaft horizontal position. An upper part of the opening 10 serves as a refrigerant passage 4a and a lower part of the opening serves as a refrigerant accumulation part 4b. The refrigerant discharge amount is adjusted by an adjustment valve 9.

Description

  The present invention relates to a stator structure for a rotating electrical machine, and more particularly to a cooling structure for a stator of a rotating electrical machine.

  Conventionally, cooling structures for rotating electrical machines or motor generators have been proposed. For example, in Patent Document 1 shown below, in a rotating electrical machine in which a coil end portion is formed as a region in which a coil extends in the axial direction from an axial end portion position of a stator, a coolant for cooling the coil end portion And a plurality of cooling liquid supply ports provided in the middle of the flow path for supplying the cooling liquid to the surface of the coil end portion, and connected to the cooling liquid supply port for cooling. It is disclosed to provide a guide for transmitting the coolant flowing out from the liquid supply port.

  In Patent Document 2, in the motor generator cooling structure, a refrigerant inlet is formed below the cooling jacket provided at the front end and the rear end of the stator core, respectively, and a refrigerant outlet is formed above each cooling jacket. However, it is disclosed that the refrigerant flows from below to above in each cooling jacket.

  Further, in Patent Document 3, in a rotating electrical machine, a cooling medium reservoir that covers at least a part of a coil end is provided at one side position or both side positions of the coil end protruding from both end faces of the stator core, and a cooling medium is provided at the coil end. It is disclosed that the cooling medium supply port to be supplied is set at a position higher than the center position of the coil end.

JP 2004-180376 A JP 2005-323416 A JP 2005-130588 A

  In Patent Document 1, since the supply of the cooling liquid to the coil is natural dripping from the cooling liquid tank, the fluid velocity on the coil surface is relatively slow and it is difficult to improve the cooling performance. Further, since a part of the dropped cooling liquid falls as it is below the outer edge of the coil, there is a problem that the whole amount of the cooling liquid is not effectively used for cooling.

  In Patent Document 2, since the refrigerant passage is in an oil-tight state, the pressure loss is increased as compared with dripping cooling due to the viscous resistance when the oil passes. In addition, since it is necessary to increase the oil flow rate in order to improve the cooling performance, it is necessary to reduce the cross-sectional area of the flow path or increase the flow rate, which causes a problem of further increasing the pressure loss. .

  In Patent Document 3, although the coil under the supply port has high cooling performance when dropped directly below the oil supply port, the coil is not supplied over the entire coil surface, and the other portions have low cooling performance and cause temperature distribution. In particular, the temperature distribution in the low flow rate region becomes significant. Further, since there is no means for adjusting the discharge amount at the oil discharge port, the liquid level of the oil reservoir greatly fluctuates due to the fluctuation of the oil supply amount, and the cooling performance of the portion other than the immersion surface is greatly deteriorated. .

  The objective of this invention is providing the structure which can cool the whole coil of the stator of a rotary electric machine efficiently.

  The present invention relates to a stator structure of a rotating electrical machine, wherein a stator core, a stator coil wound around the stator core, a refrigerant case covering coil ends of the stator coil protruding on both sides of the stator core, and the refrigerant case, A refrigerant inlet provided vertically above, a refrigerant outlet provided vertically below the refrigerant case, and an opening provided between the refrigerant inlet and the refrigerant outlet of the refrigerant case; And a discharge flow rate adjusting valve provided at the refrigerant discharge port.

  In one embodiment of the present invention, the opening is provided between the refrigerant inlet and a rotary shaft horizontal position of the rotating electrical machine.

  In another embodiment of the present invention, the opening is provided at the same position as a horizontal position of the rotating shaft of the rotating electrical machine.

  In another embodiment of the present invention, in the refrigerant case, a vertically upper part from the opening constitutes a refrigerant passage, and a vertical lower part from the opening constitutes a refrigerant reservoir.

  In another embodiment of the present invention, the discharge flow rate adjustment valve adjusts the discharge amount so that the height of the coolant level in the coolant reservoir is maximized.

  In another embodiment of the present invention, the inner diameter of the refrigerant case constituting the refrigerant passage is set smaller than the inner diameter of the refrigerant case constituting the refrigerant reservoir.

  In another embodiment of the present invention, a plurality of the openings are provided at the same horizontal position.

  In another embodiment of the present invention, a plurality of the refrigerant inlets are provided at equal intervals along the circumference of the cylindrical stator.

  ADVANTAGE OF THE INVENTION According to this invention, the stator coil of the stator of a rotary electric machine can be cooled efficiently. In particular, according to the present invention, it is possible to cool the coil end efficiently while reducing pressure loss by using both dripping cooling and immersion cooling.

It is sectional drawing of the rotary electric machine in 1st Embodiment. It is the top view seen from the axial direction of the rotary electric machine in 1st Embodiment. It is a block diagram of the refrigerant | coolant discharge | emission amount adjustment valve in 1st Embodiment. It is a graph which shows the relationship between a refrigerant | coolant flow volume and a pressure loss. It is the top view seen from the axial direction of the rotary electric machine in 2nd Embodiment. It is the top view seen from the axial direction of the rotary electric machine in 3rd Embodiment. It is the top view seen from the axial direction of the rotary electric machine in 4th Embodiment. It is a system configuration figure of a 5th embodiment. It is a top view in the case of performing only dripping cooling as a comparative example. It is a perspective view of the stator in 6th Embodiment. It is a cross-sectional perspective view in FIG. It is an enlarged view of the refrigerant | coolant inlet_port | entrance in 7th Embodiment. It is a perspective view which shows the refrigerant path in 8th Embodiment. It is a top view of the stator in 10th Embodiment. It is a section perspective view of the stator in a 10th embodiment. It is a perspective view which shows the refrigerant path in 10th Embodiment. It is a perspective view which shows the refrigerant path in 11th Embodiment. It is a top view which shows the refrigerant | coolant inlet position and refrigerant | coolant outlet position in 12th Embodiment. It is a graph which shows the coil temperature distribution in a conventional structure.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

<First Embodiment>
FIG. 1 shows a cross-sectional view of a rotating electrical machine (motor or generator) in the present embodiment. FIG. 2 shows a plan view seen from the axial direction of the rotating electrical machine.

  The rotating electrical machine includes a stator formed by winding a coil a plurality of times around a cylindrical stator core 1 made of laminated steel sheets, a rotor 6 disposed with respect to the stator via an air gap, and a rotation provided to the rotor 6. And an electric shaft 7.

  Refrigerant cases 4 that cover the coil ends 3 are formed at positions on both sides of the coil ends 3 that protrude from both end faces of the stator core 1. The refrigerant case 4 has an arcuate planar shape that covers the coil end 3 over the entire circumference, and is fixed to the stator core 1 by welding, bonding, or the like. A refrigerant inflow port 2 is formed vertically above the refrigerant case 4, more specifically, at the uppermost vertical part, from which refrigerant such as oil is supplied. Furthermore, a refrigerant discharge port 8 is provided vertically below the refrigerant case 4, more specifically, at the lowest vertical portion, and a refrigerant discharge amount adjusting valve 9 is provided at the refrigerant discharge port 8.

  On the other hand, as shown in FIG. 2, a refrigerant passage opening 10 is formed in a part of the refrigerant case 4. In the figure, the refrigerant passage opening 10 is formed at a position of approximately 90 ° in the horizontal direction with the vertical lower end as a reference. In other words, the refrigerant passage opening 10 is formed in the same horizontal plane as the rotating electrical machine shaft 7. By the refrigerant passage opening 10 formed in a part of the refrigerant case 4, the refrigerant case 4 is functionally separated from the refrigerant passage opening 10 into a vertically upper refrigerant passage 4a and a refrigerant reservoir 4b. The refrigerant flowing in from the refrigerant inlet 2 flows through the refrigerant passage 4a, cools the stator coil, and accumulates in the refrigerant reservoir 4b. The refrigerant stored in the refrigerant reservoir 4b is discharged from the refrigerant discharge port 8 to the outside. The discharge amount to the outside is adjusted by the refrigerant discharge amount adjusting valve 9.

  FIG. 3 shows an example of the refrigerant discharge amount adjusting valve 9. The refrigerant discharge amount adjusting valve 9 has a plunger. The plunger is urged by a spring in the valve seat direction (upward in the figure) and energizes the electromagnetic coil to resist the urging force of the spring from the valve seat. It is driven in a separating direction (downward in the figure). In a normal state, the plunger comes into contact with the valve seat by a spring force, and the refrigerant stays in the refrigerant reservoir 4b. On the other hand, when discharging, the electromagnetic coil is energized to move the plunger away from the valve seat against the spring force, and the refrigerant is discharged from the refrigerant reservoir 4b. The refrigerant discharge amount adjusting valve 9 adjusts the refrigerant discharge amount so that the liquid level position of the refrigerant reservoir 4b is maximized. By this adjustment, the fluctuation of the refrigerant liquid level in the refrigerant reservoir 4b due to the fluctuation of the refrigerant flow rate is absorbed and the refrigerant liquid level becomes constant, so that the stator coil temperature rise due to the liquid level drop is suppressed.

  Thus, in this embodiment, since the opening part 10 was formed in a part of the refrigerant case 4 and the atmosphere opening part was formed, the refrigerant passage part and the refrigerant reservoir part were formed. Compared with the case where the refrigerant passage is used, the pressure loss can be greatly reduced. That is, in the sealed shape, the pressure loss increases due to the viscous resistance during the circulation of the refrigerant. However, by opening the opening 10 to the atmosphere, the existence ratio of the refrigerant reservoir 4b can be limited or adjusted to prevent the pressure loss. .

  In FIG. 4, the pressure loss in the case of this embodiment and the case of a sealing shape is shown. In the figure, the horizontal axis indicates the refrigerant flow rate, and the vertical axis indicates the pressure loss. In the sealed shape, the pressure loss increases due to viscous resistance as the refrigerant flow rate increases, but in this embodiment, the pressure loss is constant regardless of the refrigerant flow rate. The maximum pressure loss in the present embodiment is the water head from the refrigerant discharge port 8 to the refrigerant reservoir liquid level, and when the refrigerant discharge amount adjusting valve 9 is adjusted so that the liquid level position of the refrigerant reservoir 4b is maximized. Since the liquid surface height is substantially equal to the formation height H of the opening 10, the maximum pressure loss ΔP = γH, where γ is the specific gravity of the refrigerant.

  In the present embodiment, the coil end 3 of the stator coil is cooled by dripping cooling in the refrigerant passage 4a, and the coil end 3 of the stator coil is cooled by immersion cooling in the refrigerant reservoir 4b. It is suppressed. That is, as shown in FIG. 9, in the configuration in which the refrigerant reservoir 4 b does not exist and only the cooling by dropping the refrigerant is performed, the refrigerant falls freely as it is below the outer edge of the coil end 3, so that it is not used effectively. However, in this embodiment, the lower part than the opening 10 can be immersed and cooled by the refrigerant reservoir 4b, and the temperature distribution of the coil end 3 can be reduced by effectively using the refrigerant after dripping cooling.

  The stator coil is wound around the stator core 1, and the coil heat of the portion of the stator coil wound around the side surface of the stator core 1 is released through the stator core, but the coil end 3 protrudes from the stator core. Therefore, it is difficult for heat to escape and the temperature rises easily. In this embodiment, since this coil end 3 is coat | covered with the refrigerant | coolant case 4, it can prevent that a refrigerant | coolant jumps out after a collision with a coil surface, and can cool the coil end 3 effectively.

Second Embodiment
In the first embodiment, one refrigerant inlet 2 is provided at the vertical top of the refrigerant case 4 (one for each coil end at each end, two as a whole), but a plurality of refrigerant inlets 2 are provided. It may be provided.

  In FIG. 5, the top view seen from the axial direction of the rotary electric machine in this embodiment is shown. A refrigerant inlet 2 is provided at the uppermost part of the refrigerant case 4, and in addition to this, two refrigerant inlets 2 are further provided. The three refrigerant inlets 2 are vertically above the refrigerant passage opening 10 and are arranged at equal intervals along the circumferential direction.

  Thus, by providing a plurality of refrigerant inlets 2 and supplying refrigerant from these refrigerant inlets 2, the stator coil can be cooled more efficiently. Also in this embodiment, similarly to the first embodiment, the coil end 3 of the stator coil is cooled by dripping cooling vertically above the refrigerant passage opening 10, and the stator coil is cooled by immersion cooling vertically below the refrigerant passage opening 10. The coil end 3 is cooled.

<Third Embodiment>
In the above embodiment, the refrigerant case 4 is provided with only one refrigerant passage opening 10, but the refrigerant passage openings 10 may be provided at a plurality of places.

  In FIG. 6, the top view seen from the axial direction of the rotary electric machine in this embodiment is shown. Two refrigerant passage openings 10 are provided on the left and right. The two refrigerant passage openings 10 are formed at the same height, and are formed at a position of 90 ° from the vertical lower end, in other words, in the same horizontal plane as the rotating electrical machine shaft 7.

  Also in the present embodiment, the vertical upper portion of the two refrigerant passage openings 10 forms the refrigerant passage 4a, and the vertical lower portion forms the refrigerant reservoir 4b, so that the stator coil can be efficiently used while suppressing pressure loss. Can be cooled.

<Fourth embodiment>
In the third embodiment, the refrigerant case 4 is provided with the two refrigerant passage openings 10. Similarly, the refrigerant case 4 is provided with the two refrigerant passage openings 10, and the upper and lower parts of the refrigerant passage opening 10. The inner diameters of the refrigerant cases 4 may be different from each other.

  In FIG. 7, the top view seen from the axial direction of the rotary electric machine in this embodiment is shown. In the figure, the inner diameter of the vertically upper refrigerant case 4 is relatively smaller than the inner diameter of the vertically lower refrigerant case 4. Therefore, the refrigerant passage 4a constituted by the refrigerant case 4 in the upper vertical portion has a smaller inner diameter than the refrigerant reservoir 4b constituted by the refrigerant case 4 in the lower vertical portion, so that the refrigerant flowing through the refrigerant passage 4a is reliably transferred to the refrigerant reservoir 4b. Supplied.

<Fifth Embodiment>
FIG. 8 shows an overall configuration diagram of a cooling system using the rotating electrical machine of the present embodiment. This is a system when mounted on a vehicle. A rotating electrical machine 11 as a motor generator is provided in a transaxle 12 including a differential gear 13. The cooled refrigerant discharged from the refrigerant discharge port 8 through the refrigerant discharge amount adjusting valve 9 of the rotating electrical machine 11 is supplied to the heat exchanger 15. The refrigerant cooled by the heat exchanger 15 is stored in the oil pan 16 in the transaxle 12. The refrigerant stored in the oil pan 16 is conveyed to the refrigerant inlet 2 of the rotating electrical machine 11 by the oil pump 14 and is circulated again as a coolant for cooling the stator coil of the rotating electrical machine 11.

  Thus, by providing the refrigerant discharge port 8 from the rotating electrical machine 11 at one place, the flow rate and heat management of the refrigerant can be facilitated, and the refrigerant circulation system including the heat exchanger 15 can be simplified.

<Sixth Embodiment>
FIG. 10 is a perspective view of a stator of a rotating electrical machine (motor or generator) in the present embodiment. Further, FIG. 11 shows a perspective view when cut along a cut surface passing through the refrigerant inlet 101 in FIG.

  Refrigerant cases 501 and 601 that cover the coil ends are formed at positions on both sides of the coil ends of the stator coil protruding from both end faces of the stator core. The refrigerant cases 501 and 601 cover the coil ends at both ends around the entire circumference to form a liquid-tight annular space. The refrigerant cases 501 and 601 are fixed to the stator core by welding, adhesion, or the like. Refrigerant inlets 101 and 201 are formed vertically below the refrigerant cases 501 and 601, respectively, and refrigerant outlets 102 and 202 are formed vertically above the refrigerant cases 501 and 601, respectively. The refrigerant inlet 101 and the refrigerant outlet 102 of the refrigerant case 501 are formed at positions that face each other by 180 °, and the refrigerant inlet 201 and the refrigerant outlet 202 of the refrigerant case 601 are also formed at positions that face each other by 180 °. Refrigerant such as cooling oil flows in the refrigerant cases 501 and 601 from vertically downward to vertically upward, cools the coil end by heat exchange with the coil end, and is discharged from the refrigerant outlets 102 and 202, respectively. Although not shown in the figure, the cooled refrigerant discharged from the refrigerant outlets 102 and 202 is radiated by the heat exchanger and then circulated and supplied to the refrigerant inlets 101 and 201 again as a low-temperature refrigerant.

  The point that the annular refrigerant cases 501 and 601 are provided so as to cover the coil ends is the same as in the above-mentioned Patent Document 2, but in the above-mentioned Patent Document 2, the flow passage cross-sectional area of the refrigerant jacket corresponding to the refrigerant cases 501 and 601 Is substantially constant from the refrigerant inlets 101 and 201 to the refrigerant outlets 102 and 202, so that the heat transfer coefficient at the coil end is uniform from the refrigerant inlets 101 and 201 to the refrigerant outlets 102 and 202. Gradually increases toward the refrigerant outlets 102 and 202, and reaches a maximum temperature at the refrigerant outlets 102 and 202 (see FIG. 19).

  On the other hand, in this embodiment, the passage cross-sectional area in the vicinity of the refrigerant inlets 101 and 201 of the refrigerant cases 501 and 601 is relatively increased than the passage cross-sectional area of the refrigerant outlets 102 and 202. In other words, the passage sectional area on the refrigerant outlet side is set to be relatively smaller than that on the refrigerant inlet side. Specifically, the position of the refrigerant inlets 101 and 201 is 0 °, the position of the refrigerant outlets 102 and 202 is 180 °, and the angle from the position of the refrigerant inlets 101 and 201 along the refrigerant outlets 102 and 202 is 60 ° to 60 °. By expanding the refrigerant cases 501 and 601 in the outer circumferential direction up to 80 °, the flow passage cross-sectional area of the refrigerant cases 501 and 601 is increased, and the refrigerant case does not spread from 60 ° to 80 ° to the positions of the refrigerant outlets 102 and 202 in the outer circumferential direction. The passage cross-sectional areas of 501 and 601 are made relatively small.

  Thus, by increasing the passage cross-sectional area in the vicinity of the refrigerant inlets 101 and 201 more than the passage cross-sectional area in the vicinity of the refrigerant outlets 102 and 202, the flow rate in the vicinity of the refrigerant inlets 101 and 201 is reduced to lower the heat transfer coefficient. Then, the temperature at the inlet of a part of the refrigerant is supplied as it is to the downstream coil. Further, since the passage cross-sectional area is relatively reduced in the vicinity of the refrigerant outlets 102 and 202, the flow velocity of the refrigerant is increased correspondingly, and the stator coil can be effectively cooled. As a result, the coil temperature on the downstream side, that is, the refrigerant outlet side is lowered, and the temperature difference between the coil temperature on the refrigerant inlet side and the coil temperature on the refrigerant outlet side is reduced.

  In this case, the coil temperature of the refrigerant inlets 101 and 201 is relatively increased as compared with the case where the flow path is not expanded in the outer circumferential direction, but the temperature flowing in from the surroundings is low in the vicinity of the refrigerant outlets 102 and 202. Since the refrigerant and the refrigerant in contact with the stator coil are merged, and the effect of increasing the flow velocity is combined to greatly improve the cooling performance, the coil temperature decreases as a whole.

  In the present embodiment, by reducing the temperature in the vicinity of the refrigerant outlets 102 and 202 where the coil temperature becomes the maximum temperature, a margin can be provided for the heat resistant temperature of the coil insulating material. Therefore, the reliability of the rotating electrical machine is improved. Furthermore, since there is room for the heat-resistant temperature, an improvement in output can be expected as a result.

<Seventh embodiment>
FIG. 12 is a partially enlarged view of the refrigerant inlet 101 of the stator in the present embodiment. In the present embodiment, in addition to the passage cross-sectional area in the vicinity of the refrigerant inlet 101 of the refrigerant case 501 being relatively larger than the passage cross-sectional area of the refrigerant outlet 102 as in the first embodiment, In the vicinity of the refrigerant inlet 101, a guide 90 that prevents the refrigerant from colliding with the coil end 40 like a jet and guides a part of the refrigerant downstream in a low temperature state is provided along the circumferential direction. A slit is formed in the guide 90 at a position facing the refrigerant inlet 101. The refrigerant is supplied to the coil end 40 through the slit, and the coil end 40 is cooled.

  The guide 90 may be locally provided in the vicinity of the refrigerant inlet 101, but the position of the refrigerant inlet 101 is 0 °, the position of the refrigerant outlet 102 is 180 °, and the guide 90 is directed from the refrigerant inlet 101 toward the refrigerant outlet 102. It can also extend from 0 ° to 80 °. The amount of refrigerant supplied to the coil end 40 can be controlled by the opening of the slit provided in the guide 90. Further, a part of the refrigerant supplied from the refrigerant inlet 101 can be detoured by the guide 90 and guided downstream of the coil end 40, and the cooling performance on the refrigerant outlet 102 side in combination with the increase in the flow velocity of the refrigerant downstream. Is further improved.

  Although FIG. 12 shows the refrigerant inlet 101 formed in the refrigerant case 501, the same applies to the refrigerant inlet 201 formed in the refrigerant case 601, and a guide is provided near the refrigerant inlet 201 in the refrigerant case 601. And a slit can be provided in the position facing the refrigerant | coolant inlet 201, and a part of refrigerant | coolant can be guide | induced to a downstream in the state with low temperature.

  The extension length along the circumferential direction of the guide 90 provided in the refrigerant case 501 and the guide provided in the refrigerant case 601 may be the same or different.

<Eighth Embodiment>
FIG. 13 is a cross-sectional perspective view of the refrigerant case 502 in the present embodiment. Like the refrigerant case 501 of the first embodiment, the refrigerant case 502 of the present embodiment has a refrigerant inlet 101 vertically downward and a refrigerant outlet 102 vertically upward, and the refrigerant flows vertically upward from vertically downward. A bypass path 92 is formed along the outer periphery from the refrigerant inlet 101 to the middle of the path from the refrigerant outlet 102, and a part of the refrigerant introduced from the refrigerant inlet 101 is a bypass path in addition to the main path. It flows into 92. Since the bypass path 92 does not contact the coil end 40 of the stator coil, the low temperature state is maintained as it is. A junction 93 with the main path is provided at a predetermined position between the refrigerant inlet 101 and the refrigerant outlet 102, and the refrigerant flowing through the bypass path 92 and the refrigerant flowing through the main path merge and flow downstream. On the downstream side, that is, on the refrigerant outlet 102 side, the passage cross-sectional area is relatively small, so that the flow velocity increases and the refrigerant having a low temperature joined from the bypass path 92 is included. The coil temperature on the 102 side is lowered.

  Here, it is desirable to set the junction of the bypass path 92 within a range of 60 ° to 80 ° from the refrigerant inlet 101. The reason why the confluence is set in the range of 60 ° to 80 ° is as follows. That is, as shown in FIG. 19, the temperature gradient is relatively large from the refrigerant inlet to 90 °, and the temperature gradient is relatively small at 90 ° or more. Therefore, it is effective to improve the cooling performance in the vicinity of 90 ° from the refrigerant inlet. For this purpose, it is desirable that the refrigerant having a low temperature is merged from the bypass path 92 at 60 ° to 80 ° immediately before 90 °. Because.

  Although the refrigerant case 502 as a modification of the refrigerant case 501 is shown in the figure, similarly, a bypass path can be provided along the outer periphery of the refrigerant case 601 as well.

<Ninth Embodiment>
In the seventh embodiment, the guide 90 is provided in the vicinity of the refrigerant inlet 101. However, since the refrigerant introduced from the refrigerant inlet 101 is supplied to the coil end 40 through the slit, the pressure loss increases in this portion. There is a fear. Therefore, a front chamber can be provided between the refrigerant inlet 101 and the guide 90, and the refrigerant can be introduced using the front chamber as a buffer space. The refrigerant temporarily stored in the front chamber is distributed to the refrigerant that flows to the coil end 40 side through the slit of the guide 90 and the refrigerant that passes through the outside of the guide 90.

<Tenth Embodiment>
In each of the above embodiments, the refrigerant passage is widened in the outer circumferential direction of the refrigerant cases 501 and 601 (or in the radial direction of the annular refrigerant cases 501 and 601). It is also possible to widen the refrigerant passage in the axial direction of 501 and 601 (the rotational axis direction of the rotating electrical machine).

  14, 15 and 16 show the configuration of the refrigerant case in the present embodiment. 14 is a plan view of the refrigerant cases 801 and 901, FIG. 15 is a perspective view taken along the line BB of FIG. 14, and FIG. 16 is a perspective view extracted along the center line C of FIG.

  The refrigerant case 801 has a refrigerant inlet 101 vertically below and a refrigerant outlet 102 vertically above. In the refrigerant case 801, the refrigerant passage extends along the axial direction at the refrigerant inlet 101, and the expanded refrigerant passage is maintained in a range of 60 ° from the refrigerant inlet 101 toward the refrigerant outlet 102. Then, the refrigerant passage expanded in the axial direction gradually narrows from 60 ° to 135 °, and the refrigerant passage becomes narrowest from 135 ° to 180 °. In FIG. 14, the size of the refrigerant passage cross-sectional area is shown as 0 ° to 60 ° as “gap large” region, 60 ° to 135 ° as “gap gradually changing region”, and 135 ° to 180 ° as “small gap” region. ing. Further, FIG. 16 shows that the refrigerant passage 110 has the largest gap in the vicinity of the refrigerant inlet 101 and thus has the largest cross-sectional area, and has the smallest gap in the vicinity of the refrigerant outlet 102 and has the smallest sectional area. ing.

Here, the reason why 135 ° to 180 ° is “small gap” is as follows. That is, as shown in FIG. 19, the coil temperature difference is relatively small from the refrigerant inlet to 90 ° to the refrigerant outlet. Therefore, even if the gap is fixed to a certain value within this range, the temperature difference is not affected, and the intermediate position of 90 ° to the refrigerant outlet is set to 135 °.

  The refrigerant case 901 is similar to the refrigerant case 801, and has a refrigerant inlet 201 vertically below and a refrigerant outlet 202 vertically above. In the refrigerant case 901, the refrigerant passage extends along the axial direction at the refrigerant inlet 201, and the expanded refrigerant passage is maintained in a range of 60 ° from the refrigerant inlet 201 toward the refrigerant outlet 202. Then, the refrigerant passage expanded in the axial direction gradually narrows from 60 ° to 135 °, and the refrigerant passage becomes narrowest from 135 ° to 180 °.

  Also in this embodiment, the flow rate in the vicinity of the refrigerant inlets 101 and 201 can be reduced to lower the heat transfer coefficient, and the refrigerant can be supplied to the downstream stator coil while maintaining the inlet temperature of a part of the refrigerant. In addition, since the passage cross-sectional area decreases in the vicinity of the refrigerant outlets 102 and 202, the flow velocity of the refrigerant increases correspondingly, and the stator coil can be efficiently cooled downstream.

<Eleventh embodiment>
In the tenth embodiment, the refrigerant passage cross-sectional area is formed so as to be reduced in the axial direction from the refrigerant inlets 101 and 201 to the refrigerant outlets 102 and 202. Thus, it is possible to provide a guide for narrowing the refrigerant passage and guiding the refrigerant to the outer peripheral side.

  FIG. 17 is a perspective view of the refrigerant case 801 in this case. A guide 111 is provided in the refrigerant passage, and the guide 111 is adjusted so that the refrigerant passage narrows from the outer periphery toward the inner periphery. As a result, a relatively larger amount of refrigerant is introduced to the outer peripheral side than the inner peripheral side on the downstream side, and the cooling performance on the outer peripheral side is improved.

  Thus, the reason why the guide 111 is provided on the downstream side and the refrigerant passage narrows from the outer peripheral side toward the inner periphery is as follows. That is, as shown in FIG. 19, the coil temperature is relatively higher at the outer periphery than at the inner periphery at all the circumferential positions from the refrigerant inlet to the refrigerant outlet. In order to improve the cooling performance on the outer peripheral side compared with the inner peripheral side and reduce the coil temperature difference between the inner peripheral side and the outer peripheral side by enlarging the throttle on the inner peripheral side and supplying the refrigerant to the outer peripheral side. It is.

<Twelfth embodiment>
In each of the embodiments described above, the refrigerant inlets 101 and 201 are formed vertically below the refrigerant case, and the refrigerant outlets 102 and 202 are formed vertically above the refrigerant case. Can be adjusted in relation to the height of the coil end.

  That is, as shown in FIG. 18, if the height of the coil ends 30 and 40 on the refrigerant inlets 101 and 201 side with respect to the stator core 70 is F, the height G of the refrigerant inlets 101 and 201 with respect to the stator core 70 is assumed. Is formed at a position that is at least ½ of the height F of the coil ends 30 and 40. Thereby, the flow of the refrigerant | coolant which hits the coil ends 30 and 40 by the side of an entrance can be decreased, and cooling of the coil ends 30 and 40 can be suppressed in the refrigerant | coolant inlet_port | entrance 101 and 201 vicinity.

  Further, assuming that the height of the coil ends 30 and 40 on the refrigerant outlets 102 and 202 side is D, the height E of the refrigerant outlets 102 and 202 is not more than ½ of the height D of the coil ends 30 and 40. Form in position. Thereby, a flow can be actively formed near the roots of the coil ends 30 and 40 of the refrigerant outlets 102 and 202, and the cooling performance can be improved.

<Other embodiments>
As mentioned above, although embodiment of this invention was described, this invention is not limited to this, A various change is possible.

  For example, in the first embodiment, one refrigerant inlet 2 is provided, and in the second embodiment, three refrigerant inlets 2 are provided, all of which have a jet structure to jet the refrigerant and introduce it into the refrigerant passage 4a. It can be configured. By using the refrigerant inlet 2 as a jet outlet, the refrigerant velocity on the stator coil surface can be improved and the wettability of the entire stator coil surface can be improved. As a result, the cooling performance can be improved.

  In the present embodiment, the refrigerant passage opening 10 is formed at a position 90 ° from the vertical lower end (lowermost part) or in the same horizontal plane as the rotating electrical machine shaft 7, but is not necessarily limited to this position. Instead, it can be formed at an arbitrary angular position. However, in order to increase the cooling efficiency by using the refrigerant without waste by the refrigerant reservoir 4b, it is desirable to form in the range from the same horizontal plane as the rotating electrical machine shaft 7 to the uppermost part of the coil end 3, which improves the refrigerant efficiency. From the standpoint of reducing the pressure loss, it is more desirable to form it at a position 90 ° from the vertical lower end (lowermost part).

  In the present embodiment, the coolant passage opening 10 is formed so as to cut the cooling case 4 in the radial direction. However, the coolant passage opening 10 is formed only in a part of the cooling case 4, and the coolant passage 4a and the coolant reservoir 4b are provided. Some of the openings 10 may be connected without being separated from each other at the position where the opening 10 is formed. In short, the refrigerant case 4 may be opened to the atmosphere through the refrigerant passage opening 10.

  Further, in the sixth embodiment, the refrigerant passage cross-sectional area in the vicinity of the refrigerant inlets 101 and 201 is made relatively larger than that on the outlet side by widening the flow path in the outer peripheral direction in the vicinity of the refrigerant inlets 101 and 201, and the tenth embodiment. Then, by expanding the flow path in the axial direction in the vicinity of the refrigerant inlets 101 and 201, the refrigerant passage cross-sectional area in the vicinity of the refrigerant inlets 101 and 201 is relatively larger than that on the outlet side, but these can also be combined. That is, the flow path is widened in the outer peripheral direction in the vicinity of the refrigerant inlets 101 and 201, and the refrigerant passage cross-sectional area in the vicinity of the refrigerant inlets 101 and 201 is relatively larger than that on the outlet side by widening the flow path in the axial direction. Also good.

  Moreover, in the form shown in FIG.14, FIG15 and FIG.16, although the clearance gap is large from the refrigerant | coolant inlet_port | entrance 101,201 to the range of 0 degree-60 degrees, this range can be set arbitrarily. The same applies to the range with a small gap. For example, the gap may be large from 0 ° to 80 °, the gradually changing range may be from 80 ° to 110 °, and the gap may be small from 110 ° to 180 °.

  In the above embodiment, the refrigerant inlet is provided vertically below the refrigerant case, and the refrigerant outlet is provided vertically above. However, the refrigerant inlet may be provided vertically above and the refrigerant outlet may be provided vertically below. In this case, the refrigerant passage cross-sectional area of the refrigerant case may be set so as to decrease sequentially from the refrigerant inlet to the refrigerant outlet.

  Furthermore, the rotating electrical machine in the present embodiment can be mounted on a hybrid vehicle or an electric vehicle as a motor or a generator, but is not necessarily limited to being mounted on a vehicle.

  1 Stator core, 2 Refrigerant inlet, 3 Coil end, 4 Refrigerant case, 4a Refrigerant passage, 4b Refrigerant reservoir, 6 Rotor, 7 Rotating electrical machine shaft, 8 Refrigerant discharge port, 9 Refrigerant discharge amount adjusting valve, 10 Refrigerant passage opening, 101, 201 Refrigerant inlet, 102, 202 Refrigerant outlet, 110 Refrigerant passage, 111 guide, 501, 502, 601, 801, 901 Refrigerant case.

Claims (8)

A stator structure of a rotating electric machine,
A stator core;
A stator coil wound around the stator core;
A refrigerant case covering a coil end of the stator coil protruding on both sides of the stator core;
A refrigerant inlet provided vertically above the refrigerant case;
A refrigerant outlet provided vertically below the refrigerant case;
An opening provided between the refrigerant inlet and the refrigerant outlet of the refrigerant case;
An exhaust flow rate adjusting valve provided at the refrigerant outlet;
A stator structure for a rotating electrical machine, comprising: In the stator structure of the rotating electrical machine according to claim 1,
The opening is provided between the refrigerant inlet and a rotary shaft horizontal position of the rotating electrical machine. A stator structure of a rotating electrical machine. In the stator structure of the rotating electrical machine according to claim 2,
The opening is provided at the same position as a horizontal position of the rotating shaft of the rotating electrical machine. In the stator structure of the rotating electrical machine according to claim 1,
A stator structure for a rotating electrical machine, wherein, in the refrigerant case, an upper part vertically from the opening constitutes a refrigerant passage, and a lower part vertically from the opening constitutes a refrigerant reservoir. In the stator structure of the rotating electrical machine according to claim 4,
The discharge flow rate adjusting valve adjusts a discharge amount so that a height of a coolant level in the coolant reservoir is maximized. In the stator structure of the rotating electrical machine according to claim 4,
A stator structure for a rotating electrical machine, wherein an inner diameter of a refrigerant case constituting the refrigerant passage is smaller than an inner diameter of a refrigerant case constituting the refrigerant reservoir. In the stator structure of the rotating electrical machine according to claim 1,
A plurality of the openings are provided at the same horizontal position. A stator structure of a rotating electrical machine. In the stator structure of the rotating electrical machine according to claim 1,
A plurality of the refrigerant inlets are provided at equal intervals along the circumference of the cylindrical stator.

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