JP2010200578A - Rotary electric machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary electric machine cooled by a gap-pickup cooling system capable of ensuring cooling performance of a rotor cooled by the gap-pickup cooling system, achieving a simplified structure, improving productivity, and producing it at low cost. <P>SOLUTION: A ventilating passage 8 is formed for ventilating a cooling medium 6 into a conductor 7 serving as the field coil of the rotor 3. In a wedge 19 mounted in the outer periphery of the rotor to fix the field coil, an air-intake hole 10 is formed to guide the cooling medium 6 in an air gap between the rotor and a stator into the ventilating passage 8. On the outer surface of the wedge 19, an intake-air guiding passage 26 is formed to guide the cooling medium into the air-intake hole 10. The intake-air guiding passage 26 is arranged circumferentially at the upstream of the air-intake hole 10 in the rotor from the stream of the cooling medium in the air gap. The intake-air guiding passage 26 is directed from the upstream side of the wedge towards its downstream to communicate with the air-intake hole 10 at the downstream side, and changes to widen its passage width in the axial direction of the rotor from the downstream side towards the upstream side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotating electrical machine including a ventilation mechanism that cools a rotor (rotor) such as a turbine generator with a cooling medium.

  Generally, in a rotating electrical machine such as a turbine generator, an air passage is provided in a stator (stator) or rotor, and air or hydrogen as a cooling medium is circulated through the air passage to generate heat due to Joule loss or iron loss. A structure for cooling a coil or an iron core (core) is known. Since the cooling performance of the rotor is high, a direct cooling system that cools the coil by contacting it with a cooling medium is widely used, but a structure that can achieve both large capacity and low cost is required. Has been. There is a tendency to increase the axis for large capacity.

  Here, a typical conventional structure will be described with reference to FIGS.

  FIG. 12 is a longitudinal sectional view showing a schematic configuration of a turbine generator provided with a gap pickup cooling type rotor used in a large capacity machine as an example of a rotating electric machine.

  The turbine generator 1 includes a rotor 3 fixed to the rotor shaft 4 and a stator 2 disposed outside the rotor 3 via an air gap 9. The air gap 9 is a gap provided between the inner peripheral surface of the stator 2 and the outer peripheral surface of the rotor 3.

  The stator 2 has a stator core 12 and a stator coil 14.

  As shown in FIG. 15, the rotor 3 includes a rotor core (rotor core) 30, a plate type field coil (laminated conductor) 7 inserted in each slot 31 of the rotor core, and a field magnet. It has a built-in wedge 19 at the top of the slot 31 to secure the coil. A clear page block 20 is disposed between the field coil 7 and the wedge 19 to electrically insulate them from each other.

  The field coil 7 and the wedge 19 are formed with a plurality of oblique channels 8 (8a, 8b) for circulating a cooling medium such as air or hydrogen. That is, the field coil 7 is configured by laminating a plurality of conductors having a plurality of oblique ventilation holes in the radial direction, and the ventilation holes of the respective layer conductors communicate with each other so that the ventilation current flows in the field coil 7. It has the structure in which the diagonal flow path 8 used as a path | route is formed.

  In the oblique flow path 8, for example, the cooling medium flows from an intake hole 8 ′ provided in the end face of the field coil 7 and is discharged to the air gap 9 through the exhaust hole 11 provided in the outer surface of the wedge 19. The cooling medium flows in from the air inlet 10 provided on the outer surface of the air flow path 8a and the wedge 19 (the wedge is not shown in FIG. 12 and shown in FIG. 15), and the exhaust hole 11 provided on the outer surface of the wedge. And a V-shaped ventilation channel 8b that is discharged to the air gap 9 through the air gap 9.

  FIG. 13 is a schematic plan view of the laminated conductor of the field coil 7 used in the large capacity machine. FIG. 14 is a view showing a longitudinal section of a V-shaped ventilation channel formed by laminating the conductors of the field coil 7, and FIG. 14A shows the radial direction (R direction) -circumferential direction (Θ). (B) is a two-dimensional cross-sectional view in the radial direction (R direction) -axial direction (Z direction). In FIG. 14B, the flow path shape of the V-shaped ventilation flow path 8b formed in the laminated conductor of the field coil 7 through the intake hole 10 and the exhaust hole 11 of the wedge 19 is easily understood. Only the flow path is shown in white. Here, a plurality of ventilation holes to be ventilation channels 8 are arranged in each laminated conductor of the field coil 7 in the circumferential direction (Θ direction) of the rotor 3 and arranged in a plurality in the axial direction (Z direction) of the rotor. An example to be shown. The two rows of ventilation holes 8 provided in each conductor of the field coil 7 and the intake holes 10 and the exhaust holes 11 provided in the wedge 19 are arranged so that the holes are in contact with each other.

  In this example, the groups of the intake holes 10 and the groups of the exhaust holes 11 are alternately arranged. As shown in FIG. 14, corresponding to the intake holes 10 and the exhaust holes 11, the V-shaped ventilation channels 8 b are formed so as to communicate from the intake holes 10 in one row to the exhaust holes 11 in the other row. Yes.

  On the other hand, the stator core (stator core) 12 of the stator 2 has a plurality of stator cooling ducts 13 corresponding to the groups of the rotor intake holes 10 and the exhaust holes 11 in the radial direction of the stator core. (R direction). These stator cooling ducts 13 form a forward zone 18 in which the cooling medium 6 flows radially outward in the stator cooling duct 13 and a reverse zone 17 in which the cooling medium 6 flows radially inward.

  An axial fan 5 is disposed on a part of the end side of the rotor shaft 4. Further, the generator 1 includes a main (first) cooler 15 and an auxiliary (second) cooler 16 for cooling the cooling medium 6 raised in temperature by cooling each part. A cylindrical body 34 that partitions the reverse zone 17 and the forward zone 18 is provided so as to surround the stator 2.

  A cooling medium (for example, hydrogen, a flow is indicated by an arrow) 6 is blown to each part of the turbine generator 1 by an axial fan 5. Specifically, a part of the cooling medium is sent from the intake port 8 ′ at one end of the rotor coil (laminated conductor) 7 to the ventilation passage 8 a by the axial fan 5. The remainder of the cooling medium 6 cools the end of the stator coil 14 and then flows into the auxiliary cooler 15 via the cooling medium duct 16a. The cooling medium recooled by the auxiliary cooler 16 flows into each stator cooling duct 13 in the reverse zone 17, cools the iron core 12 and the stator coil 14, and is discharged into the air gap 10. The cooling medium 6 is guided to an oblique flow path 8 (8b: ventilation flow path) from an intake hole 10 provided on the outer surface of the rotor 3 and flows obliquely inward to cool the field coil 7. Thereafter, the cooling medium 6 changes its direction at the bottom of the field coil 7, flows obliquely outward through the ventilation channel 8 b to cool the field coil 7, and is discharged into the air gap 9 from the exhaust hole 11. Is done. The cooling medium 6 discharged into the air gap 9 flows into each stator cooling duct 13 in the forward zone 18, cools the iron core 12 and the stator coil 14, and then flows into the main cooler 15 to be cooled. Then, a circular flow returning to the axial fan 5 is formed.

  FIG. 15 is a bird's-eye view showing a conventional example of a portion where the intake / exhaust holes on the surface of the gap pickup cooling type rotor are adjacent to each other. The wedge 19 is a fixing member for preventing the field coil 7 inserted in the slot 31 of the rotor 3 from moving due to centrifugal force. The rotation of the rotor 3 causes a flow of the cooling medium 6 in the circumferential direction of the rotor relative to the rotation of the rotor on the surface of the rotor 3. An intake guide channel 21 for guiding the cooling medium 6 flowing on the surface of the rotor 3 to the intake hole 10 is provided on the outer surface of the rotor 3. The intake guide channel 21 is formed by combining a ventilation groove (inclined groove) 22 provided on the surface of the wedge 19 and a ventilation groove (inclined groove) 23 provided on the surface of the rotor core 30. That is, the intake guide channel 21 has a structure formed when the wedge 19 is installed in the rotor 3. In addition, the intake guide channel 21 communicates with the intake hole 10 provided in the wedge 19.

  16 is a longitudinal sectional view of the air intake structure of the gap pickup cooling type rotor in FIG. The intake mechanism of the cooling medium 6 by the gap pickup will be described with reference to FIG.

  When the rotor 3 rotates, a relative circumferential direction (Θ direction) flow of the cooling medium 6 is generated in the air gap 9. The flow of the cooling medium 6 generated in the air gap 9 has a speed corresponding to the peripheral speed based on the rotational speed and diameter of the rotor 3. The peripheral speed is about 100 to 200 m / s.

  In the conventional structure, in order to efficiently guide the cooling medium 6 having such a high speed to the intake hole 10, the intake guide flow path 21 oriented in the circumferential direction of the rotor is provided on the surface of the rotor 3. As shown in FIG. 15, the opening width in the axial direction of the intake guide channel 21 is the same as the diameter of the intake hole 10, and the circumferential channel length is about five times the distance of the diameter of the intake hole 10. Have

  With respect to the circumferential flow of the cooling medium 6 in the air gap 9, a flow gradually moving from the most upstream portion of the intake guide flow channel 21 toward the intake hole 10 through the intake guide flow channel 21 is formed. However, since the inertial force is strong because the peripheral speed of the surface of the rotor 3 is fast, and the flow path length of the intake guide flow path 21 is short, the flow toward the intake hole 10 is difficult to be formed.

  In that case, the cooling medium 6 cannot be guided to the field coil 7 in the rotor 3, and the cooling performance of the field coil 7 may be insufficient. In the conventional structure, a sufficient flow path length of the intake guide flow path 21 is secured by the ventilation groove 22 on the surface of the wedge 19 and the ventilation groove 23 on the surface of the rotor 3. Further, the ventilation grooves 22 and 23 are provided with an inward slope in the radial direction (R direction) so as to gradually generate a radially inward flow to stably guide the cooling medium 6 to the intake hole 10. .

  The cooling medium 6 guided to the intake hole 10 flows in the direction of colliding with the downstream inner wall surface of the intake hole 10, the static pressure is recovered as it approaches the inner wall surface, and a pressure increasing region 24 is generated in the intake hole 10. That is, the dynamic pressure of the cooling medium 6 is converted into a static pressure. Therefore, as the speed of the cooling medium 6 toward the intake hole 10 increases, the increase in static pressure in the pressure increasing region 24 increases. The flow of the cooling medium 6 in the field coil 7 is formed by the pressure difference between the pressure increasing area 24 of the intake hole 10 and the exhaust hole 11. Therefore, in order to improve the cooling performance of the field coil 7, it is important to introduce more cooling medium 6 into the field coil 7.

  In the conventional structure, a structure in which more cooling medium 6 in the air gap 9 is sucked into the intake hole 10 by the intake guide passage 21 having a long passage length in the circumferential direction provided on the surfaces of the rotor 3 and the wedge 19. It has become.

  According to the gap pickup cooling type rotor having the above-described structure, the intake / exhaust structure for guiding the cooling medium 6 in the air gap 9 into the field coil 7 for cooling can be repeated in the axial direction. . Therefore, a plurality of similar cooling paths can be realized with respect to the axial direction of the field coil 7, the rotor 3 can be elongated, and there is an advantage that the capacity can be increased. However, in order to ensure a sufficient flow rate of the cooling medium 6 into the field coil 7, it is necessary to provide the intake guide passage 21 having a long passage length on the surface of the rotor 3. Therefore, it is necessary to process not only the wedge 19 but also the surface of the rotor 3, which increases the number of steps for manufacturing the rotor 3 and makes it difficult to reduce the cost.

  Further, a structure described in Japanese Patent Laid-Open No. 10-178754 is known as a structure for increasing the intake flow rate of the cooling medium 6 into the field coil 7. The outline is shown in FIG. In FIG. 17, (a) is a bird's-eye view of the intake section, and (b) is a cross-sectional view. This conventional structure is characterized in that a protrusion 25 is provided on the rotor 3 surface on the downstream side of the intake hole 10. According to this structure, it is possible to cause the cooling medium 6 flowing in the air gap 9 to collide with the inner surface of the protrusion 25 protruding from the rotor 3 and guide the cooling medium 6 into the intake hole 10. It becomes possible to guide more cooling medium 6 into the intake hole 10 by using the height of the protrusion 25. Therefore, there is a possibility that a sufficient intake air flow rate of the cooling medium 6 can be secured to cool the field coil 7 even if the ventilation guide flow path provided in the outer peripheral portion of the rotor 3 is shortened. Thereby, there is a possibility that the ventilation groove of the rotor 3 can be eliminated and the number of manufacturing steps can be reduced.

  However, in order to install the protrusion 25 on the surface of the rotor 3, when inserting the long rotor 3 into the stator 2, damage to equipment due to the contact of the protrusion 25 with the inner surface of the stator 2 and assembly man-hours. May increase.

Japanese Patent Laid-Open No. 10-178754 JP 2000-139050 A

  The gap pickup cooling type rotor having a conventional structure has a large number of manufacturing steps due to the complexity of the ventilation structure, and tends to be expensive. It is an object of the present invention to provide a gap pickup cooling type rotating electrical machine that can ensure the cooling performance of a gap pickup cooling type rotor, simplify the structure, improve the manufacturability, and reduce the cost. is there.

  In order to achieve the above object, the present invention constitutes an intake guide flow path for guiding the cooling medium into the field coil only by processing the wedge surface portion installed on the outer peripheral portion of the rotor. Further, the intake guide flow path is arranged at the upstream portion of the intake hole in the circumferential direction of the rotor with respect to the flow of the cooling medium in the air gap between the stator and the rotor, and downstream from the upstream side of the wedge. The air intake hole communicates with the air intake hole on the side. Further, the intake guide flow path has a structure in which the flow path width in the rotor axial direction changes so as to expand from the downstream side toward the upstream side.

  According to the gap pickup cooling system rotor of the rotating electrical machine having the intake structure of the present invention, the cooling medium flowing on the rotor surface (air gap) can be intensively taken into the intake holes from a wide area. Thereby, even if the intake guide flow path is short in the circumferential direction of the rotor, a sufficient intake air flow rate of the cooling medium for cooling the field coil can be secured. Therefore, the intake guide channel can be configured only by processing the wedge surface portion, and the number of manufacturing steps of the rotor can be reduced and the cost can be reduced as compared with the prior art.

  As a result, for example, the object of reducing the cost of a gap pickup cooling type rotor used in a large-capacity generator can be realized without impairing the cooling performance of the field coil.

The bird's-eye view which showed the intake / exhaust structure in Example 1 of this invention. 2A is a cross-sectional view of the wedge portion of the intake structure of the first embodiment, and FIG. 2B is a partial top view of the intake structure as viewed from the upper surface of the wedge. Schematic plan view of the laminated conductor of the field coil of the present invention 4A is a two-dimensional cross-sectional view in the radial direction (R direction) -circumferential direction (Θ direction) showing the ventilation channel of the present invention, and FIG. 4B is the radial direction (R direction) −. The two-dimensional sectional view of an axial direction (Z direction). FIG. 3 is a top view of the intake structure according to the first embodiment when viewed from the upper surface of the wedge, and is a view in which the range in the length direction of the wedge is expanded from FIG. FIG. 6A shows a second embodiment of the present invention, and FIG. 6A is a cross-sectional view of the wedge portion of the intake structure, and FIG. 6B is a partial top view of the intake structure as viewed from the upper surface of the wedge. The bird's-eye view of the intake / exhaust structure of Example 2 of this invention. FIG. 10 is a partial top view of a wedge showing a modification of the second embodiment. The bird's-eye view which shows the intake / exhaust structure in Example 3 of this invention. FIG. 10 is a bird's-eye view showing a modification of the intake / exhaust structure of the third embodiment. The partial top view of the wedge which shows the intake structure of Example 4 of this invention. Explanatory drawing which showed the longitudinal cross-section structure outline of the turbine generator provided with the gap pick-up mixed flow cooling system rotor of the prior art example. Schematic plan view of conventional field coil laminated conductor 14A is a two-dimensional cross-sectional view in the radial direction (R direction) -circumferential direction (Θ direction) showing the V-shaped ventilation channel of the above-described conventional example, and FIG. R direction) -Axis direction (Z direction) two-dimensional sectional view. The bird's-eye view which shows the intake / exhaust structure of the said prior art example. Sectional drawing which shows the intake structure of the said prior art example. FIG. 17A is a bird's-eye view showing a conventional intake structure different from the conventional example, and FIG. 17B is a cross-sectional view thereof.

  A first embodiment of the present invention will be described with reference to FIGS.

  FIG. 1 is a partially enlarged bird's-eye view showing an intake / exhaust portion and an intake guide channel structure of a gap pickup cooling type rotor according to a first embodiment. 2A is a sectional view of the wedge portion of the intake structure, and FIG. 2B is a partial top view of the intake structure as viewed from the upper surface of the wedge. FIG. 3 is a schematic plan view of a laminated conductor of a field coil to which the first embodiment of the present invention is applied. FIG. 4 is a diagram showing a two-dimensional cross section of the ventilation channel formed by laminating the conductors of the field coil. FIG. 4A shows the radial direction (R direction) -circumferential direction (Θ direction). A two-dimensional cross-sectional view, (b) is a two-dimensional cross-sectional view in the radial direction (R direction) -axial direction (Z direction). In FIG. 4B, only one flow path is shown so that the flow path shape of the ventilation flow path 8 formed in the laminated conductor of the field coil 7 through the intake hole 10 and the exhaust hole 11 of the wedge 19 can be easily understood. Is shown in white. Here, an example in which a plurality of ventilation holes to be ventilation channels in each laminated conductor of the field coil are arranged in a row in the circumferential direction (Θ direction) of the rotor and arranged in the axial direction (Z direction) of the rotor showed that.

  The first embodiment of the present invention is an example applied to a radial flow cooling type rotating electrical machine in which the ventilation flow path 8 in the rotor 3 is uniformly formed in the radial direction.

  In the present embodiment, the intake holes 10 and the exhaust holes 11 provided on the outer surface of the wedge 19 are alternately arranged alternately.

  Further, the configuration of the intake guide channel 26 is different from the conventional technology as follows.

  The intake guide channel 26 is provided on the outer surface of the wedge 19 in the circumferential direction of the rotor in order to guide the cooling medium 6 near the surface of the rotor 3 to the intake hole 10.

  First, the intake guide channel 26 is directed to the intake hole 10 from the upstream end side in contact with the wall of the slot 31 of the rotor 3 on the wedge 19 with reference to the circumferential flow of the cooling medium 6 flowing through the air gap. Accordingly, the groove depth changes. That is, the intake guide channel 26 has a slope structure having an inclination inward in the radial direction (R direction) of the rotor 3 as it goes downstream from the upstream side. Further, the intake guide channel 26 gradually changes its channel width in the rotor axial direction (Z direction) from the upstream end side toward the intake hole 10.

  Specifically, the upstream side of the wedge 19 (the side in contact with the rotor 3) is wider than the diameter of the intake hole 10, and the downstream side (the intake hole 10 side) becomes narrower in accordance with the diameter of the intake hole 10, The structure is in communication with the intake hole 10 at the most downstream portion.

  In FIG. 2B, the flow path widths (widths in the axial direction of the rotor) at the upstream end and the downstream end of the intake guide flow path 26 are defined as W1 and W2, respectively. Here, the maximum width W1 on the upstream end side can be taken, the width W2 on the downstream end side is made the same as the diameter of the intake hole 10, and the flow path width continuously narrows from upstream to downstream. However, a structure that changes in stages is also conceivable. Here, the maximum possible width W1 on the upstream end side will be described with reference to FIG.

  FIG. 5 is a top view of the intake structure as seen from the upper surface of the wedge, as in FIG. 2B, and is a view in which the range in the length direction of the wedge is expanded as compared with FIG. 2B.

  When the intake holes 10 and the exhaust holes 11 are alternately arranged as in the present embodiment, as shown in FIG. 5, the maximum possible upstream end width W1 of the intake guide channel 26 is the intake hole 10 and the exhaust gas. When the pitch of the holes 11 is WP, it becomes 2WP. Thus, when W1 = 2WP or W1≈2WP (where W1 <2WP) is set, the intake hole 10 may be arranged at the center of the width W3 of the wedge 19 (the circumferential width of the rotor). The length L1 of the intake guide wall 26 'of the intake guide channel 26 can be sufficiently secured in the wedge 19 (W3 / 2 << W1). W1 is preferably WP <W1 ≦ 2WP. Further, the inclination angle α of the intake guide wall 26 ′ is preferably about α = 15 to 30 degrees as an example.

  When the rotor 3 having the intake structure of the present invention is rotated, a relative circumferential direction (Θ direction) flow of the cooling medium 6 is generated in the air gap as in the conventional structure. The cooling medium 6 in the air gap 9 is guided to the intake hole 10 provided in the wedge 19 via the intake guide channel 26 and flows to the field coil 7 in the rotor 3.

  According to the structure of the present invention, since the flow path width of the intake guide flow path 26 is widened on the upstream end side in contact with the wall surface of the slot 31 of the rotor core, the cooling medium 6 near the rotor 3 surface is widened. The intake guide channel 26 can be taken from the region. Therefore, even if the flow path distance in the circumferential direction of the intake guide flow path 26 is short, a sufficient flow rate of the cooling medium 6 for cooling the field coil 7 can be secured. In addition, the intake guide channel 26 has an inward slope in the radial direction (R direction) toward the intake hole 10 on the downstream side, and the axial channel width is also changed in accordance with the diameter of the intake hole 10. Due to the structure, a flow concentrated on the intake hole 10 after the cooling medium 6 is guided to the intake guide channel 26 can be formed. That is, the cooling medium 6 taken from a wide area near the surface of the rotor 3 can be efficiently guided to the intake hole 10.

  As described above, according to the first embodiment of the present invention, the flow rate of the cooling medium 6 sufficient to cool the field coil 7 in the rotor 3 even when the radial flow path length of the intake guide flow path 25 is short. It can be secured. Therefore, the intake guide channel 26 can be configured by processing only the wedge 19, and the number of manufacturing steps for the rotor 3 can be reduced. Thereby, the effect of cost reduction of the rotor 3 can be expected. Further, by repeating the intake / exhaust structure shown in this structure in the axial direction, it is possible to easily cope with the increase in the axis of the generator, and it can be applied to increase in capacity.

  Incidentally, in the conventional structure of FIG. 15, the average cross-sectional flow velocity in the ventilation channel 8 is 15 to 25 m / s in a typical example, but in this embodiment, equal or higher is ensured. it can.

  A second embodiment of the present invention will be described with reference to FIGS.

  FIG. 7A is a sectional view of the wedge portion of the intake structure, and FIG. 7B is a partial top view of the intake structure as viewed from the upper surface of the wedge.

  The structure of the second embodiment is different from the first embodiment in that the installation position of the intake hole 10 is provided on the downstream end side in the circumferential direction (Θ direction) of the rotor. When the intake hole 10 provided in the wedge 19 is configured to penetrate from the downstream end in the circumferential direction toward the center position, the intake hole 10 has a structure that is inclined toward the inner peripheral portion in the radial direction (R direction). Since the intake hole 10 in the wedge 19 is processed using a drill, even if it has an inclined structure, it does not become difficult to manufacture and increase the number of manufacturing steps. Further, as compared with the first embodiment, the bending of the cooling medium 6 from the intake guide channel 26 to the intake hole 10 becomes larger, the flow resistance increases, and there is a possibility that the intake flow rate of the cooling medium 6 may be reduced. . However, in the series of ventilation channels from the intake hole 10 to the exhaust hole 11, there are other parts where the flow resistance is dominant, so the influence is small. The flow resistance is dominant, for example, in a connection portion (see FIG. 4) between the intake hole 10 and the ventilation path 8 in the field coil 7 where the flow path shape of the ventilation path changes significantly.

  In the second embodiment of the present invention, the installation position of the intake hole 10 of the wedge 19 is provided further downstream with respect to the circumferential direction of the rotor, so that the flow path length ΔL and the guide wall length L1 of the intake guide flow path 26 are obtained. As compared with Example 1, a structure capable of securing a longer length was realized. Since the circumferential flow path length of the intake guide flow path 26 can be made longer than that in the first embodiment, it is easy to form a flow for guiding the cooling medium 6 flowing in the circumferential direction near the surface of the rotor 3 into the intake guide flow path 26. Thus, the intake air flow rate of the cooling medium 6 can be increased as compared with the first embodiment, and the cooling performance of the field coil 7 is further improved.

  FIG. 7 is a bird's-eye view of an intake portion structure that is a modification of the second embodiment of the present invention. Reference numeral 27 denotes a notch (opening) provided in the most downstream portion of the intake guide channel 26, and this point is different from the second embodiment. When the wedge 19 is fixed to the rotor 3 by the notch 27 of the intake guide channel 26, the inner wall surface of the slot 31 in the rotor 3 appears at that portion. According to the structure of the present embodiment, the cooling medium 6 guided into the intake guide channel 26 collides with the inner wall surface of the slot of the rotor 3 that is a contact portion with the notch 27, and then the intake medium 10. Will be led to. That is, the cooling medium 6 collides with the inner wall surface of the slot of the rotor 3 and the cooling medium 6 is taken into the intake hole 10, which is equivalent to a structure in which a protrusion is installed on the downstream side of the intake hole 10. Can be obtained.

  According to the present embodiment, since the intake guide channel 26 can be processed without worrying about the contact portion of the wedge 19 with the intake hole 10, the manufacturability thereof is further improved.

  FIG. 8 is a partial top view of the wedge showing a modification of the present embodiment.

  In this embodiment, the flow path width W1 (position in contact with the coil slot) at the upstream end of the intake guide flow path 26 is adjusted to the axial direction of the air gap, and only one side in the rotor axial direction is lengthened, while the other Is the same as the position of one end of the diameter of the intake hole 10 in the rotor axial direction. When the radius of the intake hole 10 is R / 2 and the pitch between the intake hole 10 and the exhaust hole 11 is Wp, the upstream end flow path width W1 is Wp + R / 2 or a value in the vicinity thereof. According to the present embodiment, the same effects as those of the first and second embodiments can be expected, and interference with the adjacent exhaust holes 11 can be reduced as much as possible.

  A third embodiment of the present invention will be described with reference to FIGS.

  FIG. 9 is a bird's-eye view of the air intake structure of the third embodiment. The intake guide channel 28 of the present embodiment is also provided only on the surface of the wedge 19 in order to guide the cooling medium 6 in the vicinity of the surface of the rotor 3 to the intake hole 10 as in the intake guide channel 26 described so far. The intake guide flow path 28 of the third embodiment has a constant groove depth (flow path depth) from the upstream end side of the wedge 19 in contact with the rotor 3 toward the intake hole 10, that is, is flat. Is the difference. Therefore, in the structure of the present embodiment, when the wedge 19 is fixed to the rotor 3, the groove depth of the intake guide channel 28 is set at the contact portion between the most upstream portion of the intake guide channel 28 and the rotor 3. A corresponding step ΔH is formed. This step may hinder the formation of a flow that guides the cooling medium 6 flowing on the surface of the rotor 3 to the intake guide flow path 28. However, in the structure of the present invention, the flow path width in the axial direction is wide on the upstream side of the intake guide flow path 28 and the cooling medium 6 flowing on the surface of the rotor 3 can be taken in from a wide area. It is considered that the influence of the medium 6 on the intake flow rate reduction is small.

  According to the present invention, the structure of the intake guide channel 28 provided in the wedge 19 is simplified, and its manufacturability can be greatly improved.

  FIG. 10 is a bird's-eye view of an intake structure that is a modification of the third embodiment of the present invention. In this example, a cutting surface (inclined surface) 29 is provided in the vicinity of the boundary between the rotor core 30 of the rotor 3 and the upstream end of the intake guide flow path 28, and this point is different from the above-described third embodiment. Is a point. According to this structure, when the wedge 19 is fixed to the rotor 3, the most upstream portion of the intake guide flow path 28 formed in the third embodiment and the rotor 3 are formed by the inclined surface 29 provided on the rotor 3. The step of the contact portion can be avoided.

  According to the present invention, the number of manufacturing steps for providing the cutting surface 29 on the rotor 3 is required. However, since it can be handled by simple processing, an increase in cost due to this can be suppressed. The intake air flow rate of the cooling medium 6 to the intake hole 10 can be secured by simple processing.

  A fourth embodiment of the present invention will be described with reference to FIG.

  FIG. 11 is a cross-sectional view of the intake / exhaust portion structure of the fourth embodiment. Reference numeral 32 denotes an intake zone (intake hole group) formed by arranging a plurality of intake holes 10 in the axial direction of the wedge 19, and 33 denotes a plurality of exhaust holes 11 arranged in the axial direction of the wedge 19 at predetermined intervals. This is a configured exhaust zone (exhaust group). Embodiment 4 of the present invention is an example applied to a rotating electrical machine in which a plurality of intake holes 10 and exhaust holes 11 of the wedge 19 are arranged in the axial direction as shown in the prior art.

  In this embodiment in which a plurality of intake holes 10 and exhaust holes 11 are arranged in the axial direction as described above, the plurality of intake holes 10 are arranged with a gap Wp in the axial direction. In this case, the flow path width W1 at the most upstream portion of the intake guide flow path 26 is the arrangement interval Wp of the intake holes 10 at the maximum. That is, when a plurality of intake holes 10 are continuously arranged in the axial direction, the maximum possible flow path width of the flow path width W1 of the most upstream portion in the intake guide flow path 26 is W1 = Wp. The maximum flow path width W1 of the intake hole 10 is set to be equal to or less than the arrangement interval Wp, and is changed so that the flow path width becomes narrower in accordance with the diameter of the intake hole 10 toward the downstream side (the intake hole 10 side). The structure is in communication with the intake hole 10 at the most downstream portion. A preferable range of the channel width W1 is WP / 2 <W1 ≦ Wp.

Furthermore, according to the present embodiment, by forming the intake zone 32 and the exhaust zone 33 shown in FIG. 11, the reverse zone in which the flow of the ventilation passage on the stator side is radially inward, and the radially outward direction For the stator having the forward zone, the flow path structure in which the reverse zone and the intake zone 32 of the rotor 3 are respectively associated with the forward zone and the exhaust zone 33 can be configured. The number of intake holes 10 and exhaust holes 11 provided in the wedge 19 may be arbitrarily selected according to the axial length of the reverse zone or forward zone of the stator.
According to the present invention, as a whole turbine generator, a circulation pattern of the cooling medium 6 with low flow resistance can be formed, the flow rate of the cooling medium 6 circulating inside can be secured, and the cooling performance of other parts such as a stator can be improved. Can also contribute.

  If it is a rotary electric machine provided with the stator and the rotor, not only a turbine generator but the rotor is made into the air intake structure of the present invention, it is possible to realize a large capacity and cost reduction by increasing the length of the shaft.

  DESCRIPTION OF SYMBOLS 1 ... Turbine generator, 2 ... Stator (stator), 3 ... Rotor (rotor), 4 ... Rotor shaft (shaft), 5 ... Axial fan, 6 ... Cooling medium, 7 ... Field coil, 8 ... Oblique flow path (ventilation flow path), 9 ... air gap, 10 ... intake hole, 11 ... exhaust hole, 12 ... iron core (core), 13 ... stator cooling duct, 14 ... stator coil, 15 ... main cooler, DESCRIPTION OF SYMBOLS 16 ... Auxiliary cooler, 17 ... Reverse zone, 18 ... Forward zone, 19 ... Wedge, 26 ... Intake guide flow path, 27 ... Notch, 28 ... Intake guide flow path, 29 ... Cutting surface, 30 ... Rotor core, 31 ... Slot, 32 ... Intake zone, 33 ... Exhaust zone, 34 ... Cylindrical body.

Claims (8)

A rotor equipped with a field coil having a ventilation passage on the rotor side through which the cooling medium flows;
A stator that is disposed on the outer peripheral side of the rotor via an air gap, and has a stator-side ventilation channel through which a cooling medium flows;
A wedge mounted on the outer periphery of the rotor to fix the field coil;
An intake hole and an exhaust hole disposed in the wedge so as to communicate with the rotor-side ventilation channel in the field coil, and the cooling medium in the air gap is used as the intake hole of the wedge In the rotating electrical machine that cools the field coil by forming a flow that is guided into the field coil and discharged from the exhaust hole of the wedge into the air gap,
An intake guide channel is formed on the outer surface of the wedge to guide the cooling medium flowing relative to the rotation of the rotor in the air gap to the intake hole.
The intake guide flow path is disposed at the upstream portion of the intake hole in the circumferential direction of the rotor with respect to the flow of the cooling medium in the air gap, and the intake hole from the upstream side to the downstream side of the wedge Rotation characterized by having a structure in which the passage width in the rotor axial direction of the intake guide passage changes so as to expand from the downstream side toward the upstream side. Electric.   The intake guide flow path provided on the outer surface of the wedge flows in the direction from the upstream side toward the downstream side based on the flow of the cooling medium in the air gap in addition to the change in the flow path width. The rotating electrical machine according to claim 1, wherein the rotating electric machine has a slope that changes so that a depth of a groove forming the path becomes deep.   The intake guide flow path provided on the outer surface of the wedge flows in the direction from the upstream side toward the downstream side based on the flow of the cooling medium in the air gap in addition to the change in the flow path width. The rotating electrical machine according to claim 1, wherein the depth of the groove forming the path is constant.   The intake guide flow path provided on the outer surface of the wedge has a flow path width that is wider than the diameter of the intake hole on the upstream side, and narrows in accordance with the diameter of the intake hole toward the downstream side, and The rotating electrical machine according to any one of claims 1 to 3, wherein the rotating electrical machine communicates with the air intake hole.   5. The intake hole provided in the wedge is arranged near one end of the wedge on the downstream side in the circumferential direction of the rotor with reference to the flow of the cooling medium in the air gap. The rotating electrical machine according to any one of the above.   The intake guide channel provided on the outer surface of the wedge has a notch formed at one end of the downstream wedge with reference to the flow of the cooling medium flowing in the air gap, and the notch rotates. The rotating electrical machine according to claim 1, wherein the rotating electrical machine is covered by a part of a wall surface of a slot provided in the core.   Based on the flow of the cooling medium in the air gap, on the rotor outer surface portion adjacent to the upstream end of the intake guide channel provided on the outer surface of the wedge, the intake guide channel 7. An inclined surface inclined from the upstream side toward the downstream side is formed, and the outer surface of the rotor and the intake guide flow path are smoothly connected via the inclined surface. The rotating electrical machine described.   The intake holes and exhaust holes provided in the wedge are arranged on the outer surface of the wedge, with a plurality of intake holes and exhaust holes arranged in a line at a constant interval in the axial direction of the rotor. A plurality of the intake guide channels are also arranged in the axial direction according to the number of the intake holes, and the intake guide channel is wider on the upstream side than the diameter of the intake holes on the upstream side. The rotating electrical machine according to any one of claims 1 to 7, wherein the rotating electrical machine is narrower and narrows in accordance with the diameter of the intake hole toward the downstream, and communicates with the intake hole at a downstream portion.

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