JP6515074B2 - Fully enclosed outer fan type rotating electric machine - Google Patents

Description

  The present invention relates to a totally closed outer fan type rotating electric machine.

  A totally enclosed fan-shaped electric rotating machine comprises a rotor, a stator, and usually also a cooler. An outer fan is usually provided at one end (non-coupling side) of the rotor shaft of the rotor. The outside air driven by the outer fan flows into the cooling pipe from one opening of each of the cooling pipes extending in the axial direction of the cooler and flows out to the outside from the other opening.

  In the totally enclosed fan-shaped electric rotating machine, the frame and the cooler cover form a closed space. The cooling pipe passes through the inside of the closed space, and the outside of the cooling pipe is an atmosphere of the closed space. Normally, a cooling gas such as air circulates in the closed space.

  The outside air passing through the cooling pipe cools the cooling gas outside the cooling pipe. The cooling gas cools the rotor core, the stator core, the stator windings and the like.

Japanese Utility Model Publication No. 63-109560 JP 2008-172968 A

  The outside air flowing in the cooling pipe exchanges heat with the cooling gas outside the cooling pipe, and as a result of cooling the cooling gas, it receives exchange heat from the cooling gas as it flows, and the temperature rises. As a result, the temperature of the outside air in the cooling pipe is higher in the coupling side region than in the non-coupling side region to which the outer fan is attached.

  On the other hand, the flow of the cooling gas in the closed space outside the cooling pipe is usually guided by a guide plate or the like, and is substantially equal to the area on the coupling side and the area on the noncoupling side in the rotational axis direction. Flow to

  As a result, compared with the heat exchange amount in the non-bonding side region, the heat exchange amount in the bonding side region becomes lower, and the cooling efficiency as a whole of the cooler is lowered.

  As a method for making the axial temperature distribution of the stator uniform, there is known a technique in which a plurality of exhaust holes are provided along the axial direction of the frame so that the opening area of each can be adjusted (Patent Document 1) reference). There is also known a method of adjusting the air volume of each flow path by forming the flow paths divided along the axial direction on the radially outer side of the stator (see Patent Document 2).

  However, in these techniques, it is necessary to adjust the air volume of each, and when applied to the configuration of the cooler as described above, there is a problem that the structure becomes complicated, and a more simplified configuration has been desired. .

  Then, an object of the present invention is to secure the cooling efficiency of the totally closed outer fan type rotating electric machine by a more simplified structure.

In order to achieve the above-mentioned object, a totally closed outer fan-shaped electric rotating machine according to the present invention comprises a rotor shaft axially extended and rotatably supported, and a shaft for cooling gas provided radially outward of the rotor shaft. Rotation having an axial flow distribution structure for adjusting the flow distribution in the radial direction, and a rotor core provided radially outward of the axial flow distribution structure and having an axially spaced axial flow path formed therein A stator, a cylindrical stator core provided on the radially outer side of the rotor core and having a radial flow path spaced apart in the axial direction, and a stator core axially fixed in the stator core A stator having a stator winding, a frame disposed radially outward of the stator to accommodate the rotor core and the stator, and a rotor shaft axially interposed between the rotor core and the rotor core. The rotor shaft on each side Coupling side bearing and anticoupling side bearing, coupling side bearing bracket and anticoupling side bearing bracket for fixedly supporting the coupling side bearing and anticoupling side bearing respectively and connecting to the end of the frame in the axial direction; A cooler having an inner fan attached to a rotor shaft and driving the cooling gas, a plurality of cooling pipes extending in an axial direction and arranged in parallel with one another, the frame, the frame A cooler cover that forms a closed space together with the side bearing bracket and the non-coupling side bearing bracket, and an outside that is attached to the axially outer side of the non-coupling side bearing bracket of the rotor shaft and supplies outside air to the inside of the plurality of cooling pipes. And the axial flow distribution structure is axially extended to both ends and circumferentially spaced from each other to form an axial shaft with the rotor core. A radial spacer forming a flow passage, and an axial partition provided on the side farther from the outer fan as viewed from the axial center of the axial flow passage, and partitioning the axial flow passage into two parts in the axial direction and members, was closed, said radial spacers, and a plurality of recesses arranged spaced intervals to each other in the circumferential direction and extend in the axial direction an annular are formed.
Further, the totally closed outer fan type rotary electric machine according to the present invention is provided on the rotor shaft axially extended and rotatably supported, and provided radially outward of the rotor shaft to adjust the flow rate distribution of the cooling gas in the axial direction A rotor having an axial flow distribution structure, a rotor core provided radially outward of the axial flow distribution structure, and having axial flow paths spaced apart in the axial direction, and the rotor The stator core has a cylindrical stator core provided on the radially outer side of the iron core and having axial flow paths formed at intervals in the axial direction, and a stator winding axially penetrating inside the stator core. The rotor, a frame disposed outside the stator in the radial direction to accommodate the rotor core and the stator, and the rotor on both sides of the rotor shaft in the axial direction sandwiching the rotor core Coupling side bearing that supports the shaft Mounted on the rotor shaft, a non-coupling side bearing, a coupling-side bearing bracket and an anti-coupling side bearing bracket for fixedly supporting the coupling-side bearing and the non-coupling-side bearing respectively and connecting them to the end of the frame in the axial direction; A cooler having an inner fan for driving the cooling gas, a plurality of cooling pipes extending in the axial direction and arranged in parallel to one another, and the cooler, the frame, the coupling side bearing bracket and the counter It has a cooler cover which forms a closed space together with the coupling side bearing bracket, and an outer fan attached to the outside in the axial direction of the non-coupling side bearing bracket of the rotor shaft to supply outside air to the inside of the plurality of cooling pipes. The axial flow distribution structure has a diameter that extends to both ends in the axial direction and is circumferentially spaced from each other to form an axial flow path with the rotor core. A directional spacer, and an axial partition member provided on the side farther from the outer fan as viewed from the axial center of the axial channel, and partitioning the axial channel into two parts in the axial direction; The axial partition member has a cross-sectional shape and dimension corresponding to the cross-sectional shape and dimension of an axial flow passage formed by the radial spacer, and is characterized in that the axial position can be adjusted. Do.

  According to the present invention, it is possible to ensure the cooling efficiency of the totally closed outer fan-shaped rotating electric machine with a more simplified configuration.

FIG. 1 is an elevation sectional view cut along a rotation axis showing a configuration of a totally closed outer fan type rotary electric machine according to a first embodiment; It is a longitudinal cross-sectional view which shows the structure in the rotor and stator core of the totally-closed outer fan type rotary electric machine which concerns on 1st Embodiment. It is a cross-sectional view which shows the radial direction spacer of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan-shaped rotary electric machine which concerns on 1st Embodiment. It is a front view which shows the axial direction partition member of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan type rotary electric machine which concerns on 1st Embodiment. It is a front view which shows the axial direction partition member of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan type rotary electric machine which concerns on 2nd Embodiment. It is a perspective view which shows the axial direction partition member of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan type rotary electric machine which concerns on 2nd Embodiment. It is a cross-sectional view which shows the radial direction spacer of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan type rotary electric machine which concerns on 3rd Embodiment. It is a front view which shows the axial direction partition member of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan type rotary electric machine which concerns on 3rd Embodiment. It is a perspective view which shows the axial direction partition member of the axial direction flow distribution structure provided in the rotor of the totally closed outer fan type rotary electric machine which concerns on 4th Embodiment.

  Hereinafter, with reference to the drawings, a totally closed outer fan-shaped electric rotating machine according to an embodiment of the present invention will be described. Here, parts that are the same as or similar to each other are given the same reference numerals, and duplicate explanations are omitted.

First Embodiment
FIG. 1 is an elevation sectional view cut along a rotation axis showing a configuration of a totally closed outer fan type rotary electric machine according to a first embodiment. The totally closed external fan-shaped electric rotating machine 200 has a rotor 10, a stator 20, a frame 40, an anti-coupling side bearing 30a, a coupling side bearing 30b, and a cooler 60.

  The rotor 10 has a rotor shaft 11 extending horizontally in the direction of the rotation axis (hereinafter referred to as the axial direction), an axial flow distribution structure 100 provided radially outward of the rotor shaft 11, and an axial flow distribution structure. A rotor core 12 is provided at 100 radially outward.

  One end of the rotor shaft 11 in the axial direction is an object to be coupled, that is, a drive target load if the totally closed outer fan type rotary electric machine is a motor, and a coupled portion 11a coupled to a prime mover if the totally closed outer fan type electric Is formed. Hereinafter, in the axial direction, the direction of the coupling portion 11a is referred to as the coupling side, and the direction opposite thereto is referred to as the anticoupling side.

  The rotor shaft 11 is rotatably supported by the non-coupling side bearing 30a and the coupling side bearing 30b. An inner fan 51a is attached to the opposite side of the rotor core 11 with the rotor core 12 interposed therebetween in the axial direction, and an inner fan 51b is attached to the joint 11a. Further, an outer fan 55 is provided on the outer side in the axial direction of the non-coupling side bearing 30 a of the rotor shaft 11 in order to cool the totally closed outer fan-shaped rotary electric machine 200 by itself. Further, an outer fan cover 56 is attached to cover the outer fan 55. The outer fan cover 56 is formed with an inlet 56a for taking in air.

  The stator 20 is a cylindrical stator core 21 provided radially outward of the rotor core 12 via a gap 18, and a stator penetrating in the vicinity of the radially inner surface of the stator core 21 in the rotational axis direction It has a winding 22.

  The frame 40 surrounds these radial directions so as to accommodate the stator 20 and the rotor core 12. On both sides in the rotational axis direction of the frame 40, a non-coupling side bearing bracket 45a and a coupling side bearing bracket 45b are provided. The non-coupling side bearing bracket 45a and the coupling side bearing bracket 45b fixedly support the non-coupling side bearing 30a and the coupling side bearing 30b, respectively.

  A cooler 60 is provided above the frame 40. The cooler 60 includes a plurality of cooling pipes 61, a cooler cover 63, end plates 62a and 62b, and guide plates 66a and 66b. The end plates 62a support the respective non-coupling side ends of the cooling pipe 60, and the end plates 62b support the respective coupling side ends of the cooling pipe 60.

  The plurality of cooling pipes 61 are arranged parallel to one another and extend in the axial direction. Both ends of each cooling pipe 61 are open. Further, each end of each cooling pipe 61 passes through the end plates 62a and 62b, and is fixed and supported by the end plates 62a and 62b. The plurality of cooling pipes 61 are housed in the cooler cover 63.

  The frame 40, the non-coupling bearing bracket 45a, the coupling bearing bracket 45b, the cooler cover 63, and the end plates 62a and 62b together form a closed space 40a. In the cooler 60, the cooling pipe 61 is also an element forming the closed space 40a, and the outside of the cooling pipe 61 is the closed space 40a. The space on the side of the frame 40 and the space on the side of the cooler cover 63 communicate with each other at the cooler inlet opening 64 and the cooler outlet openings 65a and 65b. The cooler inlet openings 64 are provided in the axial center, and the cooler outlet openings 65a, 65b are provided on both sides in the axial direction.

  The inside of the closed space 40a is filled with a cooling gas such as air, for example. The cooling gas is driven by the inner fan 51a and the inner fan 51b to circulate in the closed space 40a. Specifically, the internal fan 51a pumps the cooling gas from the non-coupling side bearing 30a side to the rotor 10 side. Further, the internal fan 51b pumps the cooling gas from the coupling side bearing 30b side to the rotor 10 side.

  The axial flow rate distribution structure 100 is interposed between the rotor shaft 11 and the rotor core 12 in the radial direction to transmit torque between the rotor shaft 11 and the rotor core 12 and forms an axial flow path. .

  The cooling gas pumped to the rotor 10 by the internal fans 51a and 51b from the non-coupling side and the coupling side flows into the axial flow distribution structure 100 and the gap 18, and the rotor core 12 and the stator core 21 It passes with cooling and flows into the cooler 60 via the cooler inlet opening 64.

  The cooling gas flowing into the cooler 60 via the cooler inlet opening 64 rises outside the cooling pipe 61 while being cooled by the outside air inside the cooling pipe 61 between the guide plate 66 a and the guide plate 66 b. Then, it flows into the upper communication space 67. The cooling gas that has flowed into the upper communication space 67 is diverted to both axial sides, that is, to the non-coupling side and the coupling side.

  The cooling gas diverted to the opposite side is turned downward and then descends the outside of the cooling pipe 61 while being cooled by the cooling pipe 61, and flows into the frame 40 through the cooler outlet opening 65a. The cooling gas that has flowed into the frame 40 flows into the inner fan 51a and is pumped to the rotor core 12 and the stator 20 by the inner fan 51a. Thus, the cooling gas circulates in the circulation channel on the non-bonding side.

  After being diverted downward, the cooling gas branched down to the coupling side descends the outside of the cooling pipe 61 while being cooled by the cooling pipe 61, and flows into the frame 40 through the cooler outlet opening 65b. The cooling gas having flowed into the frame 40 flows into the inner fan 51 b and is pumped to the rotor core 12 and the stator 20 by the inner fan 51 b. Thus, the cooling gas circulates through the circulation flow path on the coupling side.

  As described above, the cooling gas is divided and circulated in the closed space 40 a into the two flow paths of the coupling side circulation flow path and the non-coupling side circulation flow path.

  On the other hand, the outside air is drawn into the outer fan cover 56 from the inlet 56a formed in the outer fan cover 56 by the outer fan 55, and is pumped to the inside of the plurality of cooling pipes 61 from the end plate 62a side. . The outside air passing through the inside of each of the plurality of cooling pipes 60 is first heated while cooling the cooling gas circulating in the circulation channel on the non-coupling side, and then circulated in the circulation channel on the coupling side After the temperature rises while cooling the cooling gas, it flows out of the cooling pipe 60 on the end plate 62 b side.

  FIG. 2 is a longitudinal sectional view showing the configuration in the rotor and the stator core. The axial flow distribution structure 100 has a radial spacer 110 a and an axial partition member 121. The radial spacer 110 a extends axially along the radial inside of the rotor core 12. Although the details will be described with reference to FIG. 3, the installation of the radial spacer 110a forms an axial flow passage 101a and an axial flow passage 101b as illustrated by the arrows.

  The axial flow passage 101 a and the axial flow passage 101 b are axially divided by the axial partition member 121. The axial flow passage 101 a is a flow passage on the non-coupling side from the axial partition member 121, and the axial flow passage 101 b is a flow channel on the coupling side from the axial partition member 121.

  The rotor core inner diameter direction flow path 13 is formed at intervals in the axial direction of the rotor core 12. The rotor core inner diameter direction flow passage 13 is such that the cooling gas flows radially outward from the axial flow passage 101a toward the gap 18 by a guide plate or the like (not shown) sandwiched by the steel plates constituting the rotor core 12 It is a flow path. The number and the position in the axial direction of the rotor core inner diameter direction flow path 13 are set from the temperature distribution in the rotor core 12 and the flow in the stator core 21 or the like.

  Further, a stator core inner diameter direction flow passage 23 is formed at intervals in the axial direction of the stator core 21. The stator core inner diameter direction flow path 23 is a flow such that the cooling gas flows from the gap 18 toward the radial outer side of the stator core 21 from the gap 18 by a guide plate or the like (not shown) sandwiched by steel plates constituting the stator core 21. It is a road. Although FIG. 2 shows an example in which the axial position of the stator core inner diameter direction flow passage 23 coincides with the axial position of the rotor core inner diameter direction flow passage 13, the invention is not limited thereto, and different axial direction positions may be used. . The axial number and position of the stator core radial direction flow passage 23 are set from the temperature distribution in the stator core 21 and the flow in the rotor core 12 or the like.

  FIG. 3 is a cross-sectional view showing a radial spacer of the axial flow distribution structure. The radial spacer 110 a has a plurality of circumferential partition plates 111. Each of the circumferential partition plates 111 has a radially expanded width and extends in the axial direction. The radial width of the circumferential partition plate 111 is a width corresponding to the distance between the outer surface of the concentric rotor shaft 11 and the radial inner surface of the rotor core 12.

  The plurality of circumferential partition plates 111 are attached to the rotor shaft 11 at intervals in the circumferential direction. In addition, in FIG. 3, although the case where the number of the circumferential direction dividing plates 111 is six is shown, it is not limited to this. However, since the radial spacer 110a also has a function of supporting the rotor core 12, at least three circumferential partition plates 111 are required. Moreover, since it is necessary to transmit the torque of the rotor shaft 11 to the rotor core 12, the circumferential partition plate 111 has strength necessary for this.

  The end close to the axial center in the width direction of the circumferential partition plate 111 is attached to the rotor shaft 11 by welding, for example. Moreover, in the contact part with the rotor core 12, you may provide the circumferential direction rotation stop.

  The attachment of the circumferential partition plate 111 to the rotor shaft 11 is not limited to welding. For example, one cross section in the width direction of the circumferential partition plate 111 may have a dovetail shape, and the rotor shaft 11 may have a corresponding axially extending recess to form a fitting method. Further, although the end on the side far from the axial center in the width direction of circumferential section plate 111 faces the inner surface in the radial direction of rotor core 12, it has a curved shape according to the curved surface of the inner surface of rotor core 12. It is also good.

  The circumferential partition plate 111, the rotor shaft 11, and the rotor core 12 form axial flow passages 101a and 101b extending in the axial direction.

  The circumferential partition plate 111 is divided into two parts of the circumferential partition plate 111 on the non-coupling side in the axial direction and the circumferential partition plate 111 on the coupling side by the axial partition member 121. Therefore, it divides into axial direction channel 101a and axial direction channel 101b. Here, the axial length of the circumferential partition plate 111 on the non-coupling side is longer than the axial length of the circumferential partition plate 111 on the coupling side. Therefore, in the assembled state, the axial position of the axial partition member 121 is at a position farther from the center as viewed from the side of the outer fan 55, that is, the non-coupling side.

  FIG. 4 is a front view showing an axial partition member of the axial flow rate distribution structure. The axial direction partitioning member 121 is an annular closing plate 121 a having a disk shape and having a central opening 121 b concentric with the center.

  The outer diameter of the annular closing plate 121 a is equal to the diameter of the inner surface of the rotor core 12, and the diameter of the central opening 121 b is a diameter which can be fitted to the rotor shaft 11. The annular closing plate 121 a is sandwiched in the front and rear direction by the circumferential partition plate 111 on the non-coupling side and the circumferential partition plate 111 on the coupling side.

  The operation of the present embodiment configured as described above will be described.

  The cooling gas, which is driven by the internal fan 51 a and pumped from the non-coupling side bearing 30 a side to the rotor 10 side, flows into the axial flow path 101 a or the gap 18. The cooling gas that has flowed into the axial flow passage 101a is partially advanced at the axial position where the rotor core inner diameter directional flow passage 13 is provided while advancing the axial flow passage 101a toward the axial partition member 121. And the rotor core radially inward flow channel 13 to flow radially outward.

  Similarly, the cooling gas, which is driven by the internal fan 51 b and pumped from the coupling side bearing 30 b to the rotor 10, flows into the axial flow passage 101 b or the gap 18. The cooling gas having flowed into the axial flow passage 101b is partially advanced at the axial position where the rotor core inner diameter directional flow passage 13 is provided while advancing the axial flow passage 101b toward the axial partition member 121. Flows in the radially outward direction by sequentially diverting to the plurality of rotor core radial direction flow channels 13.

  As described above, the cooling gas that has flowed radially outward through the rotor core inner diameter direction flow path 13 flows out into the gap 18. The cooling gas flowing out of the rotor core 12 and the cooling gas pressure-fed directly from the inner fans 51a and 51b to the gap 18 flow radially outward through the plurality of stator core radial direction flow paths 23, respectively.

  The cooling gas that has flowed out of the stator core 21 flows into the cooler 60 through the cooler inlet opening 64 and flows outside the cooling pipe 61 and is cooled. The cooled cooling gas passes through the cooler outlet openings 65a and 65b and descends into the frame 40, and is again pumped by the internal fans 51a and 51b.

  Since the axial flow passage 101a is longer than the axial flow passage 101b, the cooling gas passing through the rotor core 12 and the stator core 21 has a ratio of passing through the circulation flow passage on the non-coupling side is the circulation on the coupling side. Greater than the rate of passage through the flow path. Therefore, the thermal load of the cooling gas passing through the circulation channel on the non-coupling side is larger than the thermal load of the cooling gas passing through the circulation channel on the coupling side.

  On the other hand, the outside air is pumped by the outer fan 55 and flows inside the plurality of cooling pipes 61 from the non-coupling side toward the coupling side. Since the outside air flows while exchanging heat with the cooling gas outside the cooling pipe 61, the temperature rises as it flows from the non-coupling side to the coupling side.

  Thus, the cooling gas flowing in the circulation path on the opposite side of the large thermal load is cooled by the low temperature external air, and the cooling gas flowing in the circulation path on the small side of the thermal load is the high temperature. It will be cooled by the open air.

  By appropriately setting the axial position of the axial partition member 121, the inlet temperatures of the cooling gas flowing through the circulation channel on the non-coupling side and the cooling gas flowing through the circulation channel on the coupling side are equal to each other It is possible.

  That is, the temperature distribution in the axial direction of the cooling gas can be made more uniform, and the cooling efficiency can be improved.

Second Embodiment
FIG. 5 is a front view showing an axial direction partition member of an axial flow rate distribution structure provided in a rotor of a fully closed external sector rotary electric machine according to a second embodiment. FIG. 6 is a perspective view showing an axial direction partition member.

  The second embodiment is a modification of the first embodiment. The first difference from the first embodiment is that a plurality of axial partition members 122 for closing each axial flow passage is provided instead of the axial partition member 121 in the first embodiment. is there. A second point different from the first embodiment is that, in the first embodiment, the circumferential partition plate 111 is divided in the axial direction by the axial partition member 121, while the second partition is different from the first embodiment. In the embodiment, the circumferential partition plate 111 is not divided along the axial direction of the rotor core 12 but is a single body. In the other respects, the second embodiment is the same as the first embodiment.

  The shape and dimensions as viewed from the front shown in FIG. 5 of the axial direction partitioning member 122 in the second embodiment correspond to the cross sectional shape and dimensions of the axial flow channels 101a and 101b. That is, they are formed to have the same shape and size. However, the dimension is a dimension slightly smaller than the cross-sectional shape of the axial flow passage 101 b in consideration of, for example, insertion into the axial flow passage 101 b with a shorter insertion distance from the axial end of the rotor 10. Do.

  The axial partition member 122 has a sector-shaped partition closing plate 122a, two side plates 122b attached to both sides of the partition closing plate 122a, and a spring 122c attached in a compressed state between the two side plates 122b.

  The spring 122 c works to move the two side plates 122 b away from each other, and presses the two side plates 122 b against the side surface of the circumferential partition plate 111. As a result, the frictional force between the side plate 122 b and the circumferential partition plate 111 prevents the attachment position of the axial partition member 122 from being displaced in the axial direction due to the wind pressure of the cooling gas or vibration during rotation.

  The axial partition member 122 in the second embodiment configured as described above is in a state where the rotor 10 and the stator 20 are assembled when it is necessary to correct the setting of the axial position. As it is, the position can be easily adjusted by using a long jig from the axial end of the rotor 10 through the axial flow channels 101a and 101b.

Third Embodiment
FIG. 7 is a cross-sectional view showing a radial spacer of an axial flow rate distribution structure provided in a rotor of a totally closed outer sector rotary electric machine according to a third embodiment. FIG. 8 is a front view showing an axial partition member of the axial flow rate distribution structure. The shape of the axial partition member 121 is the same as that of the first embodiment.

  The third embodiment is a modification of the first embodiment. The axial flow rate distribution structure 100 in the third embodiment has a radial spacer 110 b instead of the radial spacer 110 a in the first embodiment. The radial spacer 110 b has a cylindrical shape having a thickness in the radial direction, and a plurality of flow passage forming portions 116 which are concave portions and extend in the axial direction are formed on the outer peripheral surface.

  The other points are the same as in the first embodiment. For example, as in the first embodiment, an axial partition member 121 is provided, and the radial spacer 110 b is axially divided by the axial partition member 121.

  The plurality of flow path forming portions 116 are circumferentially spaced apart from each other, and axially extend along the inner surface of the rotor core 12. As a result, a plurality of axial flow channels 102a and 102b are formed. Further, axially extending projecting portions 115 are respectively formed between the two flow path forming portions 116 adjacent to each other.

  The central opening 117 of the radial spacer 110 b is formed to mate with the rotor shaft 11. Further, a detent 118 is provided so as to prevent circumferential displacement between the rotor shaft 11 and the rotor shaft 11. The locking 118 may be performed, for example, by changing the cross section of the region fitted to the radial spacer 110b of the rotor shaft 11 from circular.

  In the axial flow rate distribution structure 100 according to the third embodiment configured as described above, the shape of the flow path forming portion 116, which is a recess, is designed from the viewpoint of securing structural strength in torque transmission and the like. There is an effect such as increasing the range of choice of

Fourth Embodiment
FIG. 9 is a perspective view showing an axial direction partition member of an axial flow rate distribution structure provided in a rotor of a fully closed external sector rotary electric machine according to a fourth embodiment. This embodiment is a combination of the radial spacer in the third embodiment and the method of the axial partition member in the second embodiment.

  That is, the shape and the dimension of the axial partition member 123 viewed from the front correspond to the cross-sectional shapes and dimensions of the axial channels 102a and 102b in the third embodiment. Here, the meaning of the correspondence is the same as that of the second embodiment.

  The axial partition member 123 has a rectangular partition closing plate 123a, two side plates 123b attached respectively to both sides of the partition closing plate 123a, and two springs 123c attached in a compressed state between the two side plates 123b. .

  The spring 123c presses the two side plates 123b against the side surface of the projecting portion 115, and the frictional force between the side plate 123b and the projecting portion 115 causes the axial partition member 123 to be attached at the wind pressure or rotation of the cooling gas. Prevent axial displacement due to vibration or the like.

  The axial partition member 123 in the fourth embodiment configured as described above is in a state where the rotor 10 and the stator 20 are assembled when it is necessary to correct the setting of the axial position. As it is, it is possible to easily adjust the position by using a long jig from the axial end of the rotor 10 via the axial flow paths 102a and 102b.

Other Embodiments
While the embodiments of the present invention have been described above, the embodiments are presented as examples and are not intended to limit the scope of the invention. For example, in the embodiment, the case of the horizontal rotation type electric rotating machine is shown as an example, but it may be the case of the standing type.

  Moreover, in each embodiment, although the case where the some axial direction flow path was mutually formed in the circumferential direction at intervals was formed was shown as an example, it is not limited to this. For example, there may be communication channels between the plurality of axial channels. Alternatively, as long as structural strength is secured as in a rigid frame structure, the elements do not have to be elements completely separated from each other as in a plate, for example.

  Furthermore, the embodiment can be implemented in various other forms, and various omissions, substitutions, and modifications can be made without departing from the scope of the invention. The embodiments and the modifications thereof are included in the invention described in the claims and the equivalents thereof as well as included in the scope and the gist of the invention.

  DESCRIPTION OF SYMBOLS 10 ... Rotor 11, 11 ... Rotor shaft, 11a ... Joint part, 12 ... Rotor core, 13 ... Rotor core inner diameter direction flow path, 18 ... Gap, 20 ... Stator, 21 ... Stator core, 22 ... Stator Winding, 23 ... stator core inner diameter direction flow passage, 30a ... anti-coupling side bearing, 30b ... coupling-side bearing, 40 ... frame, 40a ... closed space, 45a ... anti-coupling side bearing bracket, 45b ... coupling-side bearing bracket, 51a, 51b: inner fan, 55: outer fan, 56: outer fan cover, 60: cooler, 61: cooling pipe, 62a, 62b: end plate, 62c: cooling pipe through hole, 63: cooler cover, 56a ... Inlet, 64: cooler inlet opening, 65a, 65b: cooler outlet opening, 66a, 66b: guide plate, 67: upper communication space, 100: axial flow distribution structure, 101a, 101b, 102a, 102b: axial direction Path 110a, 110b: radial spacer 111: circumferential partition plate 115: projecting portion 116: flow path forming portion 117: central opening 118: anti-rotation 121: axial partition member 121a: annular closure Plate 121b central opening 122 axial partition member 122a partition closing plate 122b side plate 122c spring 123 axial partition member 123a partition closing plate 123b side plate 123c spring 200 ... Fully enclosed outer fan type rotating electric machine

Claims (4)

An axially extending rotor shaft rotatably supported, an axial flow distribution structure provided radially outward of the rotor shaft to adjust an axial flow distribution of a cooling gas, and the axial flow distribution A rotor having a rotor core provided on the radially outer side of the structure and having an axially spaced radial flow path formed therein;
A cylindrical stator core provided on the radially outer side of the rotor core and having a radial flow path formed at intervals in the axial direction, and a stator winding axially penetrating inside the stator core And a stator having
A frame disposed radially outward of the stator and housing the rotor core and the stator;
A coupling side bearing and an anticoupling side bearing for supporting the rotor shaft on both sides of the rotor shaft in the axial direction sandwiching the rotor core;
A coupled bearing bracket and a non-coupled bearing bracket for fixedly supporting the coupled bearing and the non-coupled bearing respectively and connecting them to the end of the frame in the axial direction;
An internal fan attached to the rotor shaft to drive the cooling gas;
A cooler having a plurality of cooling tubes extending axially and arranged parallel to one another;
A cooler cover which houses the cooler and which forms a closed space together with the frame, the coupling side bearing bracket and the noncoupling side bearing bracket;
An outer fan attached to the axial direction outer side of the non-coupling side bearing bracket of the rotor shaft to supply outside air to the inside of the plurality of cooling pipes;
Equipped with
The axial flow rate distribution structure is
A radial spacer extending axially to both ends and circumferentially spaced from each other to form an axial flow path with the rotor core;
An axial partition member provided on the side farther from the outer fan as viewed from the axial center of the axial channel, and partitioning the axial channel into two parts in the axial direction;
I have a,
A fully closed external sector electric rotating machine , wherein the radial spacer is annular, extends in the axial direction, and has a plurality of recessed portions spaced from each other in the circumferential direction . An axially extending rotor shaft rotatably supported, an axial flow distribution structure provided radially outward of the rotor shaft to adjust an axial flow distribution of a cooling gas, and the axial flow distribution A rotor having a rotor core provided on the radially outer side of the structure and having an axially spaced radial flow path formed therein;
A cylindrical stator core provided on the radially outer side of the rotor core and having a radial flow path formed at intervals in the axial direction, and a stator winding axially penetrating inside the stator core And a stator having
A frame disposed radially outward of the stator and housing the rotor core and the stator;
A coupling side bearing and an anticoupling side bearing for supporting the rotor shaft on both sides of the rotor shaft in the axial direction sandwiching the rotor core;
A coupled bearing bracket and a non-coupled bearing bracket for fixedly supporting the coupled bearing and the non-coupled bearing respectively and connecting them to the end of the frame in the axial direction;
An internal fan attached to the rotor shaft to drive the cooling gas;
A cooler having a plurality of cooling tubes extending axially and arranged parallel to one another;
A cooler cover which houses the cooler and which forms a closed space together with the frame, the coupling side bearing bracket and the noncoupling side bearing bracket;
An outer fan attached to the axial direction outer side of the non-coupling side bearing bracket of the rotor shaft to supply outside air to the inside of the plurality of cooling pipes;
Equipped with
The axial flow rate distribution structure is
A radial spacer extending axially to both ends and circumferentially spaced from each other to form an axial flow path with the rotor core;
An axial partition member provided on the side farther from the outer fan as viewed from the axial center of the axial channel, and partitioning the axial channel into two parts in the axial direction;
Have
The axial partition member has a cross-sectional shape and dimension corresponding to the cross-sectional shape and dimension of an axial flow passage formed by the radial spacer, and is characterized in that the axial position can be adjusted. all enclosed fan-cooled rotary electric machine you. The axial partition member includes a partition closing plate for closing an axial flow passage, two side plates vertically attached to the partition closing plate to respective end portions on both sides of the partition closing plate, and the two sheets. The fully closed external fan-shaped electric rotating machine according to claim 2 , further comprising: a spring which works to move the side plates away from each other . The radial spacer has a plurality of circumferential partition plates which extend in the radial direction and extend in the axial direction and are spaced apart from each other in the circumferential direction, and each of the plurality of circumferential partition plates is one side of the rotor The totally enclosed outer fan-shaped electric rotating machine according to any one of claims 1 to 3, which is attached to a shaft .

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