JP2017046377A - Forced air cooling type traction motor for vehicle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a forced air cooling type traction motor for vehicle which can efficiently cool inside a housing.SOLUTION: A stator 31 is fixed in a housing 10, and a rotor 43 is fixed to a rotary shaft 41. A rotary disk 60 is protruded from the rotary shaft 41 between the rotor 43 and a bearing 11. The rotary disk 60 includes a first vane 65 and a second vane 67. The first vane 65 is radially arranged on a first principal surface 60a facing the bearing 11. The second vane 67 is radially arranged on a second principal surface 60b facing the rotor 43. The housing 10 includes a vent hole 23, an inlet port 25, an exhaust port 27, and a guide plate 70. The vent hole 23 is formed at the other end in the axial direction. The inlet port 25 is formed at a position overlapping with the rotary disk 60 when viewed from the axial direction, at one end in the axial direction. The exhaust port 27 is formed at the radially outer side than the rotary disk 60 when viewed from the axial direction, at one end in the axial direction.SELECTED DRAWING: Figure 1

Description

  Embodiments described herein relate generally to a vehicle forced air cooling main motor.

  In general, in a railway vehicle, a main motor for driving wheels is attached to a carriage disposed under the floor of a vehicle body. A main motor for a railway vehicle accommodates a stator and a rotor in a housing in order to suppress entry of foreign matters such as dust.

  In the above main motor, there is a case where improvement of cooling efficiency in the housing becomes a problem.

JP 2001-238402 A

  The problem to be solved by the present invention is to provide a forced air cooling main motor for a vehicle that can cool the inside of the housing efficiently.

  The vehicle forced air-cooled main motor of the embodiment has a stator, a rotor, a bearing, and a rotating disk. The stator is fixed to the housing. The rotor is disposed in the stator and is fixed to the rotation shaft. The bearing rotatably supports the rotation shaft on one side of the rotor in the axial direction of the rotation shaft. The rotating disk protrudes from the rotating shaft between the rotor and the bearing. The rotating disk has a first blade and a second blade. The first blades are provided radially on the first main surface facing the bearing. The 2nd blade | wing is provided radially on the 2nd main surface which faces a rotor. The housing has a vent, an intake, an exhaust, and a guide plate. The vent is formed at the other end in the axial direction. The vent introduces air into the interior. The air inlet is formed at a position overlapping with the rotating disk when viewed from the axial direction at one end in the axial direction. The intake port introduces air into the interior. The exhaust port is formed at the outer end in the radial direction at the end on one side in the axial direction as compared with the rotating disk as viewed from the axial direction. The exhaust port exhausts air to the outside. The guide plate guides air so that air is discharged from the exhaust port from the intake port through the periphery of the bearing and the vicinity of the rotation shaft.

The longitudinal cross-sectional view which shows the forced air cooling main motor for vehicles which concerns on embodiment. The front view which shows a rotation disc. The longitudinal cross-sectional view which shows the forced air cooling main motor for vehicles which concerns on the 1st modification of embodiment. The longitudinal cross-sectional view which shows the forced air cooling main electric motor for vehicles which concerns on the 2nd modification of embodiment. The longitudinal cross-sectional view which shows the forced air cooling main motor for vehicles which concerns on the 3rd modification of embodiment.

  Hereinafter, a forced air cooling main motor for a vehicle according to an embodiment will be described with reference to the drawings.

FIG. 1 is a longitudinal sectional view showing a forced air cooling main motor for a vehicle according to an embodiment.
As shown in FIG. 1, a vehicle forced air-cooled main motor 1 (hereinafter simply referred to as “main motor 1”) is attached to a bogie of a railway vehicle and drives wheels. The main motor 1 is disposed in the housing 10, the stator 31 fixed to the housing 10, the rotor shaft 41 (corresponding to the “rotating shaft” in the claims), the stator 31, and fixed to the rotor shaft 41. And a rotor 43. The end of the rotor shaft 41 protrudes from the housing 10 as an output end. In the following description, a direction along the central axis O of the rotor shaft 41 is referred to as an axial direction, a direction orthogonal to the central axis O is referred to as a radial direction, and a direction around the central axis O is referred to as a circumferential direction. Further, the output end side of the rotor shaft 41 in the axial direction is referred to as a driving side (one side), and the opposite side is referred to as a counter driving side (the other side).

  The stator 31 includes a stator iron core 33 and a stator coil 35. The stator iron core 33 is formed in a cylindrical shape extending along the axial direction by stacking a plurality of annular magnetic steel plates in the axial direction. The stator core 33 is sandwiched from both sides in the axial direction by a pair of annular core pressers 37 formed in an annular shape. A pair of iron core holding | suppressing 37 is connected via the connecting plate 39 extended along an axial direction. A plurality of teeth (not shown) projecting inward in the radial direction are formed on the inner peripheral portion of the stator core 33 at intervals in the circumferential direction. Slots (not shown) are formed between the teeth. A stator coil 35 is disposed in the slot.

  The rotor 43 is disposed inside the stator 31. The rotor 43 includes a rotor core 45 that is externally fitted to the rotor shaft 41. The rotor core 45 is formed in a cylindrical shape by laminating a plurality of annular magnetic steel plates along the axial direction. The rotor core 45 is clamped from both sides in the axial direction by a pair of core pressers 47 formed in an annular shape. The entire outer peripheral surface of the rotor core 45 is opposed to the inner peripheral surface of the stator core 33 with a radial interval.

  A plurality of grooves (not shown) extending along the axial direction are formed in the outer peripheral portion of the rotor core 45 at intervals in the circumferential direction. A rotor bar 49 is embedded in each of the plurality of grooves. The driving side end and the non-driving side end of each rotor bar 49 protrude outward in the axial direction from the rotor core 45. The drive-side ends and the counter-drive-side ends of the rotor bars 49 are integrally connected by end rings 51, respectively.

  A plurality of ventilation holes 53 penetrating the rotor core 45 in the axial direction are formed in the inner peripheral portion of the rotor core 45 at intervals in the circumferential direction. In addition, each iron core retainer 47 is formed with a communication hole 55 that communicates with each other in the ventilation hole 53.

  The drive side end of the rotor shaft 41 is rotatably supported by the first bearing 11A (corresponding to “bearing” in the claims). The counter drive side end of the rotor shaft 41 is rotatably supported by the second bearing 11B.

  The housing 10 includes a first stator case 13 and a second stator case 15 that fix the stator 31, a first bearing bracket 17 that holds the first bearing 11A, and a second bearing bracket 19 that holds the second bearing 11B. It is equipped with.

  The first stator case 13 is disposed on the drive side of the stator 31 and forms a drive side end of the housing 10. The first stator case 13 is formed in a bottomed cylindrical shape having a bottom portion 13 a on the drive side, and is arranged coaxially with the rotor shaft 41. A mounting hole 13b penetrating the bottom 13a in the axial direction is formed in the bottom 13a. The inner diameter of the mounting hole 13 b is larger than the outer diameter of the rotor iron core 45. The end of the first stator case 13 on the side opposite to the driving side is connected to the driving side core pressing member 37 of the pair of core pressing members 37.

  The second stator case 15 is disposed on the counter drive side with respect to the stator 31, and forms the counter drive side end of the housing 10. The second stator case 15 is formed in a bottomed cylindrical shape having a bottom portion 15 a on the non-driving side, and is arranged coaxially with the rotor shaft 41. A mounting hole 15b is formed in the bottom portion 15a so as to penetrate the bottom portion 15a in the axial direction. The driving side end of the second stator case 15 is connected to the counter driving side iron core retainer 37 of the pair of iron core retainers 37.

  The second stator case 15 is formed with a vent 23 for introducing air into the housing 10. The vent 23 penetrates the peripheral wall portion of the second stator case 15 in the radial direction. A duct 21 is formed on the outer surface of the second stator case 15 and extends outward from the peripheral edge of the vent hole 23. A blower (not shown) is connected to the duct 21. Air blown from the blower is introduced into the housing 10 through the vent 23.

  The first bearing bracket 17 is disposed so as to close the mounting hole 13 b of the first stator case 13. The first bearing bracket 17 forms the drive side end of the housing 10 together with the first stator case 13. The first bearing bracket 17 is formed in an annular shape having an outer diameter equivalent to that of the bottom portion 13 a of the first stator case 13 when viewed from the axial direction. Moreover, the 1st bearing bracket 17 is formed in the shape which the inner peripheral part protruded toward the non-driving side in the axial direction rather than the outer peripheral part in the longitudinal cross sectional view. The first bearing bracket 17 includes a shaft holding portion 17a formed on the inner peripheral edge, a connecting portion 17b provided on the outer peripheral edge and connected to the first stator case 13, a shaft holding portion 17a, and a connecting portion 17b. And a connecting portion 17c for connecting the two.

  The shaft holding portion 17a is formed in a cylindrical shape extending along the axial direction. 11 A of 1st bearings are accommodated inside the shaft holding part 17a. The drive side end portion of the rotor shaft 41 is inserted through the shaft holding portion 17a. The shaft holding part 17a rotatably supports the rotor shaft 41 via the first bearing 11A.

  The connecting portion 17b is disposed so as to overlap the drive side surface of the bottom portion 13a of the first stator case 13. The connecting portion 17b is fastened and fixed to the bottom portion 13a of the first stator case 13 by a fastening member (not shown).

  The connecting portion 17c connects the outer edge portion of the shaft holding portion 17a and the inner edge portion of the connecting portion 17b. The inner surface 17d (surface on the non-driving side) of the connecting portion 17c extends toward the driving side as it goes from the radially inner side to the outer side.

  The second bearing bracket 19 is disposed so as to close the mounting hole 15 b of the second stator case 15. The second bearing bracket 19 together with the second stator case 15 forms the counter drive side end of the housing 10. The second bearing bracket 19 is formed in an annular shape. The 2nd bearing bracket 19 has the cylindrical shaft holding part 19a extended along an axial direction, and the flange part 19b extended toward a radial direction outer side from the outer peripheral part of the shaft holding part 19a.

  The shaft holding portion 19 a is inserted through the mounting hole 15 b of the second stator case 15. The outer diameter of the shaft holding portion 19 a is equal to the inner diameter of the mounting hole 15 b of the second stator case 15. The second bearing 11B is accommodated inside the shaft holding portion 19a. The end on the non-driving side of the rotor shaft 41 is inserted into the shaft holding portion 19a. The shaft holding portion 19a rotatably supports the rotor shaft 41 via the second bearing 11B.

  The flange portion 19 b is disposed so as to overlap the drive side surface of the bottom portion 15 a of the second stator case 15. The flange portion 19b is fastened and fixed to the bottom portion 15a of the second stator case 15 by a fastening member (not shown).

  A rotating disk 60 is disposed between the rotor 43 in the housing 10 and the first bearing 11A. The rotating disk 60 is made of, for example, a metal material. The rotating disk 60 protrudes outward from the rotor shaft 41 in the radial direction. The rotating disk 60 includes a hub 61, a main plate 63, a plurality of first blades 65, and a plurality of second blades 67. Further, the rotating disk 60 has a first main surface 60 a facing the first bearing 11 </ b> A and a second main surface 60 b facing the rotor 43.

The hub 61 is fixed to the rotor shaft 41. The end surface of the hub 61 on the side opposite to the driving side is in contact with the driving side end surface of the driving side core pressing member 47 of the pair of core pressing members 47 of the rotor 43.
The main plate 63 projects outward from the hub 61 in the radial direction. The main plate 63 is formed away from the inner surface 17d of the connection portion 17c of the first bearing bracket 17 and along the inner surface 17d. The main plate 63 extends toward the drive side from the radially inner side to the radially outer side. The outer diameter of the main plate 63 is substantially the same as the outer diameter of the rotor core 45.

FIG. 2 is a front view of the rotating disk as viewed from the drive side in the axial direction.
As shown in FIG. 2, the plurality of first blades 65 are provided on the outer peripheral portion on the first main surface 60a. Each first blade 65 is provided in a radial shape extending outward from the center of the rotating disk 60. The first blades 65 are arranged at equal intervals in the circumferential direction. The position in the radial direction of the radially outer end of each first blade 65 substantially matches the position in the radial direction of the outer peripheral edge of the main plate 63.

  The plurality of second blades 67 are provided on the outer peripheral portion on the second main surface 60b. Each of the second blades 67 is provided radially so as to extend outward from the center of the rotating disk 60. The second blades 67 are arranged at equal intervals in the circumferential direction, like the first blades 65.

As shown in FIG. 1, the housing 10 is formed with an intake port 25 for introducing air into the housing 10 and an exhaust port 27 for discharging air to the outside.
The intake port 25 is formed in the first bearing bracket 17. The air inlet 25 is formed on the opposite side of the air vent 23 (hereinafter referred to as “lower side”) across the central axis O of the rotor shaft 41 in a longitudinal sectional view passing through the center of the air vent 23. The intake port 25 is formed radially inward from the portion where the plurality of first blades 65 are located when viewed from the axial direction. The air intake 25 penetrates the first bearing bracket 17 in the axial direction. The intake port 25 is, for example, a long hole having a long axis along the circumferential direction. One intake port 25 may be formed, or a plurality of intake ports 25 may be formed.

The exhaust port 27 is formed in at least one of the first stator case 13 and the first bearing bracket 17. The exhaust port 27 has a first exhaust port 27a and a second exhaust port 27b.
The first exhaust port 27a passes through the first bearing bracket 17 and the first stator case 13 in the axial direction. The first exhaust port 27 a is formed on the opposite side of the intake port 25 (hereinafter referred to as “upper side”) across the central axis O of the rotor shaft 41 in a longitudinal sectional view passing through the center of the vent port 23. The first exhaust port 27a is formed on the outer side in the radial direction than the rotating disk 60 when viewed from the axial direction. More specifically, the opening on the non-driving side of the first exhaust port 27a is parallel to the first main surface 60a of the main plate 63 of the rotating disk 60 in a longitudinal sectional view and passes through the first blade 65. It is formed at a position that intersects the line. The first exhaust port 27a is, for example, a long hole having a long axis along the circumferential direction. One first exhaust port 27a may be formed, or a plurality of first exhaust ports 27a may be formed.

  Similarly to the first exhaust port 27a, the second exhaust port 27b penetrates the first bearing bracket 17 and the first stator case 13 in the axial direction. A plurality of second exhaust ports 27b are formed over the entire circumference so as to be along the circumferential direction on the radially outer side of the first exhaust ports 27a. More specifically, the opening on the non-driving side of the second exhaust port 27 b is parallel to the second main surface 60 b of the main plate 63 of the rotating disk 60 in a longitudinal sectional view and passes through the second blade 67. It is formed at a position that intersects the line. The second exhaust port 27b is a long hole having a long axis along the circumferential direction, for example.

  A guide plate 70 is disposed between the rotating disk 60 and the first bearing bracket 17. The guide plate 70 is disposed below the central axis O of the rotor shaft 41. The guide plate 70 is formed in a semicircular shape so as to overlap the lower half of the first bearing bracket 17 when viewed from the axial direction.

  The guide plate 70 includes a peripheral wall portion 71, an inclined wall portion 73, and an attachment portion 75. The peripheral wall 71 is provided between the plurality of first blades 65 and the air inlet 25 in the radial direction. The peripheral wall 71 is formed in a semi-cylindrical shape along the circumferential direction. The inclined wall portion 73 extends along the first main surface 60 a of the rotating disk 60 from the edge on the counter driving side of the peripheral wall portion 71 toward the inside in the radial direction. The radially inner end edge of the inclined wall portion 73 is disposed in a state where a gap is provided with respect to the outer peripheral surface of the rotor shaft 41. The attachment portion 75 extends along the inner surface 17 d of the first bearing bracket 17 from the driving side edge of the peripheral wall portion 71 toward the outer side in the radial direction. The attachment portion 75 is fastened and fixed to the first bearing bracket 17 by a fastening member (not shown).

Hereinafter, the operation of the present embodiment will be described.
In the configuration described above, when the railway vehicle travels, current is supplied to the main motor 1 via the pantograph. By supplying the supplied current to the stator coil 35, the rotor 43 and the rotor shaft 41 are rotated. At this time, a blower (not shown) connected to the duct 21 rotates. As a result, air is introduced into the space between the stator 31 and the rotor 43 and the bottom portion 15a of the second stator case 15 and the second bearing bracket 19 (hereinafter referred to as “space S1”). .

  When the rotor shaft 41 rotates, the second blade 67 also rotates. At this time, centrifugal force acts on the air between the second blades 67. The air between the second blades 67 flows from the radially inner side toward the outer side. Due to the air flow between the second blades 67, a negative pressure is generated at a portion radially inward of the plurality of second blades 67.

  Due to the negative pressure in the portion radially inward of the second blade 67 described above, the air in the space S1 passes through the ventilation hole 53 of the rotor core 45 and the communication hole 55 of the iron core retainer 47, from the non-driving side to the driving side. It flows toward. At this time, the air exchanges heat with the second bearing 11 </ b> B whose temperature increases as the rotor shaft 41 rotates through the second bearing bracket 19. Further, the air passing through the ventilation holes 53 exchanges heat with the rotor core 45 whose temperature has been increased by driving. Thereby, the 2nd bearing 11B and the rotor 43 can be cooled.

  A part of the air in the space S1 flows from the counter driving side toward the driving side through a gap between the stator iron core 33 of the stator 31 and the rotor iron core 45 of the rotor 43. At this time, the air exchanges heat with the stator iron core 33 and the rotor iron core 45. Thereby, the stator 31 can be cooled.

  The temperature of the air that has passed through the ventilation holes 53 is increased by heat exchange with the second bearing 11 </ b> B and the rotor 43. The air that has passed through the ventilation holes 53 collides with the main plate 63 of the rotating disk 60 and flows from the radially inner side to the outer side along the second main surface 60b. Thereafter, the air that has flowed along the second main surface 60b is discharged to the outside from an exhaust port 27 that is formed on the outer side in the radial direction with respect to the rotating disk 60 when viewed in the axial direction. As a result, air whose temperature has risen due to heat exchange with the second bearing 11B, the rotor core 45, and the stator core 33 can be discharged to the outside without causing heat exchange with the first bearing 11A.

  Further, when the rotating disk 60 rotates, the first blade 65 also rotates. At this time, negative pressure is generated in a space radially inward of the first blade 65 (hereinafter referred to as space “S2”) based on the same principle as that of the second blade 67 described above. When negative pressure is generated in the space S2, outside air is introduced into the space S2 through the intake port 25. The outside air flows between the inclined wall portion 73 of the guide plate 70 and the first bearing bracket 17 and flows from the radially outer side to the vicinity of the rotor shaft 41 (see arrow A1). At this time, the outside air exchanges heat with the first bearing 11 </ b> A whose temperature increases as the rotor shaft 41 rotates through the lower portion of the first bearing bracket 17.

A part of the outside air that has flowed to the vicinity of the rotor shaft 41 flows between the inclined wall portion 73 of the guide plate 70 and the rotating disk 60, and the rest flows along the outer peripheral surface of the rotor shaft 41 from the lower side to the upper side. It flows toward.
The air that flows between the inclined wall portion 73 and the rotating disc 60 flows between the inclined wall portion 73 and the rotating disc 60 from the radially inner side to the outer side (see arrow A2). Thereafter, the outside air is discharged to the outside from an exhaust port 27 formed in the lower portion of the first stator case 13 and the first bearing bracket 17.

  Further, the outside air that has flowed from the lower side toward the upper side along the outer peripheral surface of the rotor shaft 41 passes between the upper portion of the first bearing bracket 17 and the rotating disk 60 and moves from the radially inner side to the outer side. (See arrow A3). Thereafter, the outside air is discharged to the outside from an exhaust port 27 formed in the upper portion of the first stator case 13 and the first bearing bracket 17.

  According to the embodiment described above, the rotary disc 60 provided between the rotor 43 and the first bearing 11A, and the air inlet 25 formed at a position overlapping the rotary disc 60 when viewed from the axial direction. And an exhaust port 27 formed on the outer side in the radial direction with respect to the rotating disk 60 when viewed from the axial direction, and the rotating disk 60 is provided on the first main surface 60a facing the first bearing 11A. Since the first blade 65 and the second blade 67 provided on the second main surface facing the rotor 43 are provided, the temperature of the first bearing 11A is suppressed and the stator 31 and The rotor 43 can be cooled, and the first bearing 11 </ b> A can be cooled by outside air introduced from the air inlet. Therefore, the inside of the housing 10 can be efficiently cooled.

  Hereinafter, modifications of the main motor according to the embodiment will be described. In addition, the same code | symbol is attached | subjected about the same part as embodiment mentioned above, and description is abbreviate | omitted or simplified.

First, the forced air cooling main motor 101 for a vehicle according to the first modification will be described.
FIG. 3 is a longitudinal sectional view showing a forced air cooling main motor for a vehicle according to a first modification of the embodiment.
In the embodiment shown in FIG. 1, the first main surface 60a of the rotating disk 60 is exposed toward the drive side. On the other hand, the first modification shown in FIG. 3 differs from the embodiment shown in FIG. 1 in that a heat insulating material 69 is attached on the first main surface 60a of the rotating disk 60. .

  The heat insulating material 69 is preferably formed of a material having a lower thermal conductivity than that of the rotating disk 60. For example, a resin material or the like is suitable. The heat insulating material 69 is attached to the inside in the radial direction from the first blade 65 in the first main surface 60a.

  According to the first modification described above, since the heat insulating material 69 is mounted on the first main surface 60a facing the first bearing 11A of the rotating disc 60, the energized stator 31 and rotor are energized. Even when the rotating disk 60 is heated by heat exchange with the air heated by the 43 or heat transfer through the iron core retainer 45 of the rotor 43, the heat of the rotating disk 60 is the first bearing. Propagation to 11A can be prevented. Therefore, an increase in the temperature of the first bearing 11A can be suppressed, and the inside of the housing 10 can be efficiently cooled.

Next, a forced air cooling main motor 201 for a vehicle according to a second modification will be described.
FIG. 4 is a longitudinal sectional view showing a forced air cooling main motor for a vehicle according to a second modification of the embodiment.
In the embodiment shown in FIG. 1, the second exhaust port 27b is formed along the axial direction. On the other hand, in the second modified example shown in FIG. 4, the second exhaust port 127b is formed along the direction in which the main plate 63 of the rotating disk 60 projects in a longitudinal sectional view. Different from the embodiment shown.

  According to the second modification described above, the second exhaust port 127b is formed along the direction in which the main plate 63 of the rotating disk 60 projects in a longitudinal sectional view. Air flowing from the inner side to the outer side can be smoothly discharged from the second exhaust port 127b. Therefore, the inside of the housing 10 can be efficiently cooled.

Next, a forced air cooling main motor 301 for a vehicle according to a third modification will be described.
FIG. 5 is a longitudinal sectional view showing a forced air cooling main motor for a vehicle according to a third modification of the embodiment.
In the embodiment shown in FIG. 1, the air inlet 25 is formed in the lower portion of the first bearing bracket 17. On the other hand, the third modification shown in FIG. 5 is different from the embodiment shown in FIG. 1 in that the air inlets 225 are formed on both upper and lower side portions of the first bearing bracket 17. In the embodiment shown in FIG. 1, the first exhaust port 27 a is formed in the upper portion of the first stator case 13 and the first bearing bracket 17. On the other hand, in the third modification shown in FIG. 5, the first exhaust port 227 a is formed in the upper and lower side portions of the first stator case 13 and the first bearing bracket 17. It is different from the embodiment. Furthermore, in the embodiment shown in FIG. 1, the guide plate 70 is formed in a semicircular shape when viewed from the axial direction. On the other hand, the third modification shown in FIG. 5 differs from the embodiment shown in FIG. 1 in that the guide plate 270 is formed in a circular shape when viewed from the axial direction.

As shown in FIG. 5, the housing 10 is formed with an intake port 225 and an exhaust port 227.
The air inlet 225 is formed in the first bearing bracket 17. A plurality of air inlets 225 are formed over the entire circumference along the circumferential direction. The air inlet 225 is formed at a position overlapping with a portion on the radially inner side of the rotating disk 60 with respect to the portion where the plurality of first blades 65 are located when viewed from the axial direction. The intake port 225 is, for example, a long hole having a long axis along the circumferential direction.

  The exhaust port 227 has a first exhaust port 227a and a second exhaust port 27b. The first exhaust port 227a passes through the first bearing bracket 17 and the first stator case 13 in the axial direction. A plurality of first exhaust ports 227a are formed over the entire circumference along the circumferential direction. The first exhaust port 227a is a long hole having a long axis along the circumferential direction, for example.

  The vehicle forced air-cooled main electric motor 301 includes a guide plate 270. The guide plate 270 is formed in a circular shape so as to overlap the first bearing bracket 17 when viewed from the axial direction. The guide plate 270 includes a peripheral wall portion 271, a slanted wall portion 273, and an attachment portion 275.

  The peripheral wall portion 271 is provided between each first blade 65 and the air inlet 25 in the radial direction. The peripheral wall portion 271 is formed in a cylindrical shape along the circumferential direction. The inclined wall portion 273 extends along the first main surface 60a of the rotating disk 60 from the edge on the counter driving side of the peripheral wall portion 271 toward the inside in the radial direction. The inner peripheral edge of the inclined wall portion 273 is in a state where a gap is provided with respect to the outer peripheral surface of the rotor shaft 41. The attachment portion 275 extends along the inner surface 17d of the first bearing bracket 17 from the driving side edge of the peripheral wall portion 271 toward the outer side in the radial direction. The attachment portion 275 is fastened and fixed to the first bearing bracket 17 by a fastening member (not shown).

Hereinafter, the operation of this modification will be described.
When the rotating disk 60 rotates and the first blade 65 rotates, negative pressure is applied to a space radially inward of the first blade 65 (hereinafter referred to as space “S3”), as in the above-described embodiment. Occur. When negative pressure is generated in the space S3, outside air is introduced into the space S3 through the intake port 25. The outside air flows between the inclined wall portion 273 of the guide plate 270 and the first bearing bracket 17 and flows from the radially outer side to the vicinity of the rotor shaft 41 (see arrow A4). At this time, the outside air exchanges heat with the first bearing 11 </ b> A whose temperature has increased with the rotation of the rotor shaft 41 via the first bearing bracket 17.

  The outside air that has flowed to the vicinity of the rotor shaft 41 flows between the inclined wall portion 273 of the guide plate 270 and the rotating disk 60 and flows from the radially inner side to the radially outer side (see arrow A5). Thereafter, the outside air is discharged to the outside from the first exhaust port 227a.

  In the third modification described above, a plurality of intake ports 225 are formed over the entire circumference along the circumferential direction, so that more outside air can be introduced from the intake ports 225. Therefore, heat exchange with the first bearing 11A can be reliably performed, and the inside of the housing 10 can be efficiently cooled.

  In the above embodiment, the plurality of first blades 65 and the plurality of second blades 67 are arranged on the rotating disk 60 at equal intervals in the circumferential direction, but may be arranged at unequal intervals. Good.

  According to at least one embodiment described above, a rotating disk provided between the rotor and the first bearing, an intake port formed at a position overlapping the rotating disk when viewed from the axial direction, and a shaft An exhaust port formed on the outer side in the radial direction than the rotating disk when viewed from the direction, and the rotating disk has a first blade provided on the first main surface facing the first bearing; And the second blade provided on the second main surface facing the rotor, so that the stator and the rotor can be cooled while suppressing an increase in the temperature of the first bearing, and introduced from the intake port. The first bearing can be cooled by the outside air. Therefore, the inside of the housing can be efficiently cooled.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 1,101,201,301 ... Forced air cooling main motor for vehicles, 10 ... Housing, 11A ... 1st bearing (bearing), 23 ... Vent, 25, 225 ... Inlet, 27, 227 ... Exhaust, 27a , 227a ... 1st exhaust port (exhaust port), 27b, 127b ... 2nd exhaust port (exhaust port), 31 ... Stator, 41 ... Rotor shaft (rotary shaft), 43 ... Rotor, 60 ... Rotating disc, 60a ... 1st main surface, 60b ... 2nd main surface, 65 ... 1st blade | wing, 67 ... 2nd blade | wing, 69 ... Heat insulating material, 70,270 ... Guide plate

Claims (2)

A stator fixed to the housing;
A rotor disposed within the stator and fixed to a rotating shaft;
A bearing that rotatably supports the rotary shaft on one side of the rotor in the axial direction of the rotary shaft;
On the second main surface facing the rotor, the first blades extending from the rotating shaft between the rotor and the bearing, and radially provided on the first main surface facing the bearing A rotating disk provided with second blades provided radially on
With
The housing is
A vent that is formed at the other end in the axial direction and introduces air into the interior;
An air inlet that introduces air into the interior of the one end in the axial direction, which is formed at a position overlapping the rotating disk when viewed from the axial direction;
An exhaust port for discharging air to the outside, formed on the outer side in the radial direction of the rotating shaft than the rotating disk as viewed from the axial direction at the one end in the axial direction;
A guide plate configured to exhaust air from the intake port through the periphery of the bearing and the vicinity of the rotation shaft, and from the exhaust port;
A forced air-cooled main motor for a vehicle having   The forced air cooling main motor for a vehicle according to claim 1, wherein a heat insulating material is attached on the first main surface.

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