JP2010024941A - Axial flow hydraulic machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enable efficient operation by reducing a hydraulic power loss generated by water amount fluctuation. <P>SOLUTION: An axial flow hydraulic machine (axial flow waterwheel 10) comprises a waterwheel runner 11 having a plurality of runner vanes 19 elongating radially from the circumferential surface of a runner boss 18 mounted to the principal axis 17, and a discharge ring 12 disposed with a gap on the top end outer side of the runner vanes 19. The waterwheel runner 11 comprises a stabilizing member 20 between the adjacent runner vanes 19 for stabilizing the flow between the runner boss 18 and the discharge ring 12. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an axial-flow hydraulic machine having a runner including a plurality of runner vanes radially extending on a peripheral surface of a runner boss, and a discharge ring disposed on the outer side of the tip end of the runner vane.

  Axial-flow hydraulic machines include axial-flow turbines such as mixed-flow turbines, Kaplan turbines, and valve turbines. During the operation of this axial water turbine, the water flow flowing from the upstream flows through the casing, flows from the stay vane to the guide vane, flows into the runner vane of the water turbine runner, rotates the water turbine runner, and turns the generator through the main shaft of this water turbine runner. To drive. The flowing water that has flowed out of the runner vanes is led to the downstream discharge channel through the suction pipe.

  In the vicinity of the runner vane of the axial flow turbine, the opening / closing amount of the guide vane is adjusted in order to change the operation state of the turbine according to the required power generation amount. At this time, at the time of operation with a small amount of water with the guide vane opening and closing amount narrowed, the centrifugal force becomes relatively large and the flow is biased toward the outer peripheral side. On the contrary, at the time of operation with a large amount of water with a wide open / close amount of the guide vane, the centrifugal force becomes relatively small and the flow is biased toward the inner peripheral side. These fluctuations are said to be secondary flow and cause hydraulic loss.

Patent Document 1 proposes an axial flow turbine in which a thin fin is attached to an upper suction pipe of an axial flow turbine to reduce hydraulic loss.
JP-A-4-63969

  However, the axial water turbine described in Patent Document 1 is provided with a plurality of fins on the inner wall of the suction pipe on the downstream side of the discharge ring to suppress the swirling flow generated in the water flow flowing out from the runner vane of the water turbine runner, As a result, the hydraulic power loss is indirectly reduced, so it may not always be sufficient to reduce the hydraulic power loss.

  An object of the present invention is to provide an axial flow hydraulic machine capable of realizing efficient operation by reducing hydraulic loss caused by fluctuations in the amount of water.

  The present invention provides a shaft having a runner including a plurality of runner vanes radially extending on a peripheral surface of a runner boss attached to a main shaft, and a discharge ring disposed on the outer side of the tip end of the runner vane with a gap therebetween. In the hydropower machine, the runner is provided between the runner boss and the discharge ring, and between the adjacent runner vanes, rectifying means for rectifying the flow between the runner boss and the discharge ring is provided. To do.

  According to the present invention, since the rectification means rectifies the flow between the runner boss and the discharge ring, the hydraulic loss can be reduced even if the amount of water flowing between the runner boss and the discharge ring fluctuates. Efficient operation can be realized.

  The best mode for carrying out the present invention will be described below with reference to the drawings.

[A] First embodiment (FIGS. 1 to 7)
FIG. 1 is an overall configuration diagram showing an axial-flow turbine in a first embodiment to which an axial-flow hydraulic machine according to the present invention is applied. FIG. 2 is a perspective view showing the water turbine runner and the rectifier of FIG. FIG. 3 is a cross-sectional view of the turbine runner of FIG. 2 and the rectifier body together with a discharge ring. 4 is a longitudinal sectional view taken along the line IV-IV in FIG.

  As shown in FIG. 1, an axial-flow turbine 10 as an axial-flow hydraulic machine has a turbine runner 11 as a rotating portion disposed inside a discharge ring 12 as a stationary portion, and a casing on the upstream side of the discharge ring 12. 13, a stay vane 14, and a guide vane 15 for adjusting the flow rate are sequentially arranged, and a suction pipe 16 is arranged on the downstream side.

  As shown in FIGS. 2 to 4, the water turbine runner 11 includes a plurality of (for example, four) runner vanes 19 extending radially on the outer peripheral surface of a runner boss 18 attached to the main shaft 17. The runner vanes 19 are arranged at equal intervals around the runner bosses 18, and the discharge rings 12 are arranged on the outer sides of the tips of the runner vanes 19 with a gap.

  In such an axial flow turbine 10, as shown in FIG. 1, the water flow from the upper pond is accelerated by the stay vane 14 through the casing 13, the flow rate is adjusted through the guide vane 15, and the runner vane 19 of the turbine runner 11 is adjusted. After reaching the runner vane 19, it flows out to the lower pond through the suction pipe 16. The water turbine runner 11 is rotated by the action of the water flow to the runner vane 19 and the energy of the water flow is converted into rotational energy. This rotational energy is transmitted to the generator via the main shaft 17 and is converted into electric energy by driving the generator. The

  As shown in FIGS. 2 to 6, the water turbine runner 11 includes a rectifier that rectifies the water flow between the runner boss 18 and the discharge ring 12, between the runner boss 18 and the discharge ring 12, and between the adjacent runner vanes 19. As a means, a rectifier 20 is installed. One rectifier 20 is disposed at a position equidistant from the main shaft 17 between the adjacent runner vanes 19, and each rectifier 20 is formed in a curved shape along the outer peripheral surface of the runner boss 18, and is parallel to the main shaft 17. Is arranged.

  That is, the rectifying body 20 is formed by cutting the cylindrical material into a shape in which one end is adapted to the pressure surface 19A of the runner vane 19 and the other end is adapted to the negative pressure surface 19B of the runner vane 19. This rectifying body 20 is connected to the pressure surface 19A of one adjacent runner vane 19 by welding or the like in a state parallel to the main shaft 17, and the other end is welded to the negative pressure surface 19B of the other adjacent runner vane 19. Etc. are joined together. In this way, the rectifying bodies 20 are arranged between all the adjacent runner vanes 19 of the water turbine runner 11, and the same number of runners 19 are provided.

  Therefore, according to the present embodiment, the following effects (1) and (2) are obtained.

  (1) The amount of water flowing from the guide vane 15 (FIG. 1) between the runner boss 18 of the turbine runner 11 and the discharge ring 12 is changed by adjusting the opening / closing amount of the guide vane 15 and is influenced by centrifugal force. As shown by a two-dot chain line in FIG. 7, a secondary flow that does not follow the design streamline occurs due to bias toward the outer peripheral side (discharge ring 12 side) or bias toward the inner peripheral side (runner boss 18 side). In this embodiment, since the rectifier 20 is disposed between the runner boss 18 and the discharge ring 12, as shown by an arrow W in FIG. The flow (secondary flow) biased toward the circumferential side is regulated by the rectifier 20 and rectified. By suppressing the secondary flow in this way, hydraulic loss can be reduced, and as a result, efficient operation of the axial flow turbine 10 can be realized.

  (2) Since the water flow between the runner boss 18 and the discharge ring 12 is regulated and rectified by the rectifier 20, the flow separating from the outer peripheral surface of the runner boss 18 is suppressed. As a result, the occurrence of cavitation on the runner boss 18 side can be suppressed.

[B] Second embodiment (FIGS. 8 and 9)
FIG. 8 is a cross-sectional view corresponding to FIG. 3, showing a turbine runner and a rectifier of an axial water turbine according to a second embodiment to which an axial hydraulic machine according to the present invention is applied. FIG. 9 is a longitudinal sectional view taken along line IX-IX in FIG. In the second embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description will be simplified or omitted.

  The axial flow turbine 30 as the axial flow hydraulic machine of the present embodiment is different from the axial flow turbine 10 of the first embodiment in that the rectifying means arranged between the adjacent runner vanes 19 in the turbine runner 36. The shape of the rectifying body 31 and the mounting angle T1 thereof.

  That is, as shown in FIG. 8, the rectifying body 31 is formed in a spiral shape that decreases in diameter from the distal end 32 side to the proximal end 33 side of the runner vane 19 along the outer peripheral surface of the runner boss 18. Also in this rectifier 31, in each of the adjacent runner vanes 19, one end is welded to the pressure surface 19 </ b> A of the runner vane 19 and the other end is welded to the negative pressure surface 19 </ b> B of the runner vane 19. As shown in FIG. 9, the runner vane 19 is inclined from the inlet 34 side toward the outlet 35 side toward the main shaft 17 side, and the mounting angle T1 of the rectifying body 31 with respect to the main shaft 17 is in the range of 0 ° ≦ T1 ≦ 30 °. Is set.

  Therefore, according to the present embodiment, in addition to the same effects as the effects (1) and (2) of the first embodiment, the following effect (3) is achieved.

  (3) Since the rectifying body 31 is formed in a spiral shape having a diameter reduced from the tip 32 side to the base end 33 side of the runner vane 19 along the outer peripheral surface of the runner boss 18, the gap between the runner boss 18 and the discharge ring 12 is The water stream flowing through can be guided to the runner boss 18 side. Further, since the rectifying body 31 is disposed so as to be inclined toward the main shaft 17 side from the inlet 34 side to the outlet 35 side of the runner vane 19, the water flow between the runner boss 18 and the discharge ring 12 is caused to flow on the runner boss 18 on the outlet 35 side. Can lead to the side. From these things, the cavitation which arises in the runner boss | hub 18 can be suppressed further than the case of the said effect (2).

[C] Third embodiment (FIGS. 10 and 11)
FIG. 10 is a cross-sectional view corresponding to FIG. 3, showing a turbine runner and a rectifier of an axial-flow turbine in a third embodiment to which the axial-flow hydraulic machine according to the present invention is applied. 11 is a longitudinal sectional view taken along line XI-XI in FIG. In the third embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description will be simplified or omitted.

  The axial-flow turbine 40 as an axial-flow hydraulic machine in the present embodiment is different from the axial-flow turbine 10 in the first embodiment in that the number of runner vanes 19 in the turbine runner 42 and a rectifier 41 as a rectifier. And its mounting angle T2.

  That is, in the water turbine runner 42 of the axial water turbine 40, a plurality of, for example, eight runner vanes 19 are radially extended at equal intervals on the outer peripheral surface of the runner boss 18.

  Further, the rectifying body 41 has a flat plate shape and is disposed between the runner boss 18 and the discharge ring 12 so as to be inclined from the front end 32 side to the base end 33 side of the runner vane 19 between the adjacent runner vanes 19. The That is, the rectifying body 41 is formed by cutting and processing a flat plate material so that one end 43 is joined to the pressure surface 19A of the runner vane 19 and the other end 44 is fitted to the negative pressure surface 19B of the runner vane 19. Is done. One end 43 of the rectifying body 41 is joined to the pressure surface 19A of one adjacent runner vane 19 by welding or the like, and the other end 44 is joined to the negative pressure surface 19B of the other adjacent runner vane 19 by welding or the like. .

  At this time, as shown in FIG. 10, the rectifying body 41 is inclined at one end 43 toward the distal end 32 side of the runner vane 19 and the other end 44 toward the proximal end 33 side of the runner vane 19. At the same time, as shown in FIG. 11, the rectifying body 41 is inclined to the main shaft 17 side from the inlet 34 side to the outlet 35 side of the runner vane 19, and the mounting angle T2 of the rectifying body 41 with respect to the main shaft 17 is 0 °. ≦ T2 ≦ 30 ° is set.

  Therefore, according to the present embodiment, in addition to the same effects (1) and (2) as in the first embodiment, the following effect (4) is achieved.

  (4) As shown in FIG. 10, the rectifying body 41 is inclined between the runner boss 18 and the discharge ring 12 and between the adjacent runner vanes 19 from the tip 32 side of the runner vane 19 toward the base end 33 side. Since it is arranged, the water flow flowing between the runner boss 18 and the discharge ring 12 can be guided to the runner boss 18 side. Further, as shown in FIG. 11, since the rectifying body 41 is disposed to be inclined toward the main shaft 17 side from the inlet 34 side to the outlet 35 side of the runner vane 19, it is between the runner boss 18 and the discharge ring 12. Can be guided to the runner boss 18 side on the outlet 35 side. As a result, cavitation occurring in the runner boss 18 can be further suppressed than in the case of the effect (2). Moreover, since the rectifying body 41 has a flat plate shape, it is easily manufactured.

[D] Fourth embodiment (FIGS. 12 and 13)
FIG. 12A is a perspective view showing a turbine runner and a rectifier of an axial water turbine according to a fourth embodiment to which an axial hydraulic machine according to the present invention is applied, and FIG. It is a perspective view which shows the water turbine runner and rectifier of the 1st modification in embodiment of this invention, (C) is a perspective view which shows the water turbine runner and rectifier of the 2nd modification in 4th Embodiment. In the fourth embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description will be simplified or omitted.

  The axial flow turbine 50 as an axial flow hydraulic machine according to the present embodiment is different from the axial flow turbine 10 according to the first embodiment in that rectifiers 51 and 52 as rectifiers in the turbine runner 53 are adjacent to each other. It is a point partially arranged in each region between the runner vanes 19.

  That is, as shown in FIG. 12, the rectifying body 51 is disposed on the inlet 34 side portion of the runner vane 19 in each region between the adjacent runner vanes 19 (FIG. 12A), and the inlet 34 of the runner vane 19. And the outlet 35 (FIG. 12 (B); first modified embodiment) and disposed on the outlet 35 side of the runner vane 19 (FIG. 12 (C); second modified embodiment). Further, as shown in FIG. 13A, the rectifying body 51 is disposed on the inlet 34 side of the runner vane 19 in each region between the adjacent runner vanes 19 so as to protrude outward from the inlet 34 ( (3rd form).

  Further, as shown in FIG. 13B, the rectifying body 52 is directed from the pressure surface 19 </ b> A of one adjacent runner vane 19 toward the negative pressure surface 19 </ b> B of the other runner vane 19 in each region between adjacent runner vanes 19. The width dimension M is configured and arranged so as to be gradually shortened (fourth modification).

  Therefore, according to this embodiment, in addition to the same effects (1) and (2) as those of the first embodiment, the following effects (5) and (6) are achieved.

  (5) The rectifying body 51 is partially arranged in the inlet 34 side portion, the outlet 35 side portion of the runner vane 19, the substantially central portion of the inlet 34 and the outlet 35, etc. in each region between the adjacent runner vanes 19, Since it is not provided in the entire area, the cost can be reduced. Further, since the rectifying body 52 has a lower rectifying effect on the negative pressure surface 19B side of the runner vane 19 than the rectifying effect on the pressure surface 19A side, in the rectifying body 52, from one pressure surface 19A of the adjacent runner vane 19. Since the width dimension M is gradually shortened toward the suction surface 19B of the other runner vane 19, the cost can be reduced.

  (6) In the third modification, the rectifying body 51 (FIG. 13A) is arranged to project outward from the inlet 34 on the inlet 34 side of the runner vane 19 in each region between the adjacent runner vanes 19. Therefore, the turbulence of the water flow between the runner boss 18 and the discharge ring 12 can be suppressed before flowing into the space between the adjacent runner vanes 19. As a result, the flow of water between the runner boss 18 and the discharge ring 12 can be well rectified, the hydraulic loss can be further reduced, and the axial flow turbine 50 can be efficiently operated.

[E] Fifth embodiment (FIGS. 14 to 16)
FIG. 14 is a perspective view showing a turbine runner, a rectifier, and a rectifying vane of an axial flow turbine according to a fifth embodiment to which an axial hydraulic machine according to the present invention is applied. FIG. 15 is a cross-sectional view corresponding to FIG. 3, showing an axial flow water turbine provided with the water turbine runner, the rectifier, and the rectifying vanes of FIG. 14. 16 is a cross-sectional view taken along line XVI-XVI in FIG. In the fifth embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description will be simplified or omitted.

  The axial flow water turbine 60 as the axial flow hydraulic machine of the present embodiment is different from the axial flow water turbine 10 of the first embodiment in that the rectifying means in the water turbine runner 61 is the rectifying body of the first embodiment. 20 and a rectifying vane 62 provided between the rectifying body 20 and the discharge ring 12 and attached to the rectifying body 20.

  That is, the rectifier 20 is provided between the runner boss 18 and the discharge ring 12 and between the adjacent runner vanes 19, is formed in a curved shape along the outer peripheral surface of the runner boss 18, and is parallel to the main shaft 17. One end is fixed to the pressure surface 19A of one adjacent runner vane 19, and the other end is fixed to the negative pressure surface 19B of the other adjacent runner vane 19.

  Further, the rectifying vane 62 is provided between the adjacent runner vanes 19 on the outer peripheral side with respect to the curved rectifying body 20, that is, between the rectifying body 20 and the decharge ring 12, and is shaped along the shape of the runner vane 19. Thus, the rectifying body 20 is fixedly disposed by welding or the like. When the number of runner vanes 19 is N1, the number N2 of rectifying vanes 62 is set to N2 ≧ N1. When N2> N1, a plurality of rectifying vanes 62 are provided between the adjacent runner vanes 19 in the circumferential direction of the runner boss 18.

  Therefore, according to the present embodiment, the following effects (7) and (8) are obtained in addition to the effects (1) and (2) of the first embodiment.

  (7) Since the rectifier 20 and the rectifying vane 62 attached to the rectifier 20 are disposed between the runner boss 18 and the discharge ring 12, the water flow between the runner boss 18 and the discharge ring 12 is adjusted. The rectification vane 62 can be rectified together with the fluid 20. For this reason, hydraulic loss can be further reduced and efficient operation of the axial-flow turbine 60 can be realized.

  (8) Since the rectifying vane 62 fixed to the rectifying body 20 is formed along the shape of the runner vane 19 on the outer peripheral side of the rectifying body 20 between the adjacent runner vanes 19, the runner boss 18 and the discharge ring 12. The water flow flowing between them acts not only on the runner vane 19 but also on the rectifying vane 62 and causes the turbine runner 61 to generate a rotational force. As a result, the turbine efficiency can be improved even at the time of partial load with a small amount of water.

[F] Sixth embodiment (FIGS. 17 to 20)
FIG. 17 is a perspective view showing a turbine runner and a rectifying vane of an axial-flow turbine in the sixth embodiment to which the axial-flow hydraulic machine according to the present invention is applied. FIG. 18 is a longitudinal sectional view corresponding to FIG. 4, showing an axial flow water turbine provided with the water turbine runner and the rectifying vane of FIG. 17. In the sixth embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description will be simplified or omitted.

  The axial flow turbine 70 as the axial flow hydraulic machine of the present embodiment is different from the axial flow turbine 10 of the first embodiment in that the first to fifth embodiments are used as rectifying means in the turbine runner 71. This is the point that the straightening vanes 72 having the shape that follows the shape of the runner vanes 19 are provided without the straightening bodies 20, 31, 41, 51, 52 of the form.

  That is, the rectifying vane 72 is provided on the disk charge ring 12 side from the vicinity of the middle between the runner boss 18 and the discharge ring 12 and is attached to the runner boss 18 using the stay 73 or the like. As shown in FIGS. 17 and 18, one rectifying vane 72 may be provided in the circumferential direction of the runner boss 18 at an intermediate position between the runner vanes 19 in each of the adjacent runner vanes 19. One sheet may be provided close to the negative pressure surface 19B side (FIG. 19A; first modification), or a plurality of sheets may be provided in the circumferential direction of the runner boss 18 (FIG. 19B). Second variant).

  20A, the flow straightening vane 72 may be formed shorter than the runner vane 19 and arranged on the inlet 34 side of the runner vane 19 between the adjacent runner vanes 19 (third Variant). Further, as shown in FIG. 20 (B), the rectifying vane 72 is arranged on the inlet 34 side of the runner vane 19 between the adjacent runner vanes 19 and is arranged to protrude outward from the inlet 34. (4th modification).

  Therefore, according to the present embodiment, the following effects (9) and (10) are achieved.

  (9) Since the rectifying vane 72 is arranged near the middle between the runner boss 18 and the discharge ring 12 on the discharge ring 12 side, the water flow flowing between the runner boss 18 and the discharge ring 12 is rectified by the rectifying vane 72. Can be As a result, hydraulic loss can be reduced, and efficient operation of the axial water turbine 70 can be realized. In particular, in the fourth modified embodiment (FIG. 20B), since the flow straightening vane 72 is disposed on the inlet 34 side of the runner vane 19 and protrudes outward from the inlet 34, the discharge from the runner boss 18 and discharge. The turbulence can be suppressed before the water flow between the rings 12 flows into between the adjacent runner vanes 19. For this reason, it is possible to satisfactorily rectify the water flow between the runner boss 18 and the discharge ring 12 to reduce hydraulic loss.

  (10) In the case of the first modified form (FIG. 19A) in which the rectifying vane 72 is disposed close to the suction surface 19B side of the runner vane 19 between the adjacent runner vanes 19, the water flow is reduced to the suction surface 19B. By actively leading to the side, cavitation generated on the suction surface 19B of the runner vane 19 can be satisfactorily suppressed.

  As mentioned above, although this invention was demonstrated based on the said embodiment, this invention is not limited to this. For example, in the first to fifth embodiments described above, one rectifier 20, 31, 41, 51, 52 is disposed between adjacent runner vanes 19. For example, FIG. As indicated by a two-dot chain line, a plurality of rectifying bodies 20, 31, 41, 51, 52 may be installed between the runner boss 18 and the discharge ring 12 in each of the adjacent runner vanes 19.

BRIEF DESCRIPTION OF THE DRAWINGS The whole block diagram which shows the axial flow water turbine in 1st Embodiment to which the axial flow hydraulic machine which concerns on this invention was applied. The perspective view which shows the water turbine runner of FIG. 1, and a rectifier. FIG. 3 is a cross-sectional view showing the water turbine runner of FIG. 2 and a rectifier along with a discharge ring. FIG. 4 is a longitudinal sectional view taken along line IV-IV in FIG. 3. FIG. 2 is a plan view showing a part of the water turbine runner and the rectifier of FIG. FIG. 3 is a perspective view showing the water wheel runner and the rectifier of FIG. 2 as viewed from obliquely below. Explanatory drawing explaining the effect | action of a rectifier. The cross-sectional view corresponding to FIG. 3 which shows the turbine runner and rectifier of the axial-flow water turbine in 2nd Embodiment to which the axial-flow hydraulic machine which concerns on this invention was applied. The longitudinal cross-sectional view which follows the IX-IX line of FIG. The cross-sectional view corresponding to FIG. 3 which shows the turbine runner and rectifier of the axial-flow water turbine in 3rd Embodiment to which the axial-flow hydraulic machine which concerns on this invention was applied. FIG. 11 is a longitudinal sectional view taken along line XI-XI in FIG. 10. (A) is a perspective view showing a turbine runner and a rectifier of an axial flow turbine in a fourth embodiment to which an axial flow hydraulic machine according to the present invention is applied, and (B) is a first view in the fourth embodiment. The perspective view which shows the water turbine runner and rectifier of a deformation | transformation form, (C) is a perspective view which shows the water turbine runner and rectification body of the 2nd deformation | transformation form in 4th Embodiment. (A) is a perspective view showing a turbine runner and a rectifier of a third modification in the fourth embodiment, and (B) is a perspective view showing a turbine runner and a rectifier of a fourth modification in the fourth embodiment. Figure. The perspective view which shows the turbine runner, the rectifier, and the rectification vane of the axial-flow water turbine in 5th Embodiment to which the axial-flow hydraulic machine which concerns on this invention was applied. The cross-sectional view corresponding to FIG. 3 which shows the axial-flow water turbine provided with the water turbine runner of FIG. 14, a rectifier, and a rectification vane. Sectional drawing which follows the XVI-XVI line | wire of FIG. The perspective view which shows the turbine runner and rectification | straightening vane of the axial-flow water turbine in 6th Embodiment to which the axial-flow hydraulic machine which concerns on this invention was applied. The longitudinal cross-sectional view corresponding to FIG. 4 which shows the axial-flow water turbine provided with the water turbine runner and rectification | straightening vane of FIG. (A) is a perspective view showing a water turbine runner and a rectifying vane according to a first modification in the sixth embodiment, and (B) is a perspective view showing a water turbine runner and a rectification vane according to a second modification in the sixth embodiment. Figure. (A) is a perspective view showing a turbine runner and a rectifying vane according to a third modification in the sixth embodiment, and (B) is a perspective view showing a turbine Runner and a rectifying vane according to a fourth modification in the sixth embodiment. Figure.

Explanation of symbols

10 Axial flow turbine (Axial flow hydraulic machine)
11 Wheel runner 12 Discharge ring 17 Spindle 18 Runner boss 19 Runner vane 20 Rectifier (rectifier)
19A Pressure surface 19B Negative pressure surface 30 Axial flow turbine (axial flow hydraulic machine)
31 Rectifier (rectifier)
32 End 33 Base end 34 Inlet 35 Outlet 40 Axial water turbine (Axial hydraulic machine)
41 Rectifier (rectifier)
50 Axial water turbine (Axial hydraulic machine)
51, 52 Rectifier (rectifier)
60 Axial water turbine (Axial hydraulic machine)
62 Rectifying vane (rectifying means)
70 Axial water turbine (Axial hydraulic machine)
72 Rectifying vane (rectifying means)
T1, T2 Mounting angle M Width N1, N2 Number of sheets

Claims (15)

In an axial hydraulic machine having a runner including a plurality of runner vanes radially extending on a peripheral surface of a runner boss attached to a main shaft, and a discharge ring arranged with a gap on the outer side of the tip end of the runner vane. ,
An axial flow hydraulic machine characterized in that the runner is provided with rectifying means for rectifying the flow between the runner boss and the discharge ring between the runner boss and the discharge ring and between the adjacent runner vanes. . The axial flow hydraulic machine according to claim 1, wherein the rectifying means is a rectifying body that is formed in a curved shape along the peripheral surface of the runner boss and is arranged in parallel to the main shaft. 2. The axial flow hydraulic power according to claim 1, wherein the rectifying means is a rectifying body formed in a spiral shape having a diameter reduced from a distal end side to a proximal end side of the runner vane along a peripheral surface of the runner boss. machine. The axial flow hydraulic machine according to claim 1, wherein the rectifying means is a flat plate shape and is a rectifying body that is inclined from the distal end side to the proximal end side of the runner vane. The rectifying means has an attachment angle T with respect to the main shaft.
0 ° ≦ T ≦ 30 °
The axial-flow hydraulic machine according to claim 1, wherein the rectifier is set to The axial flow hydraulic machine according to claim 1, wherein the rectifying means is a rectifying body provided at an inlet side, an outlet side of the runner vane, or a substantially central position of the inlet and the outlet. The axial flow hydraulic machine according to claim 1, wherein the rectifying means is a rectifying body provided on the inlet side of the runner vane and protruding outward from the inlet. 2. The axial flow hydraulic machine according to claim 1, wherein the rectifying means is a rectifying body configured such that a width dimension becomes shorter from a pressure surface of a runner vane toward a negative pressure surface of an adjacent runner vane. The rectifying means is formed in a curved shape along the peripheral surface of the runner boss, and a rectifying body attached to the runner vane;
The axial flow hydraulic machine according to claim 1, further comprising a rectifying vane provided between the rectifying body and the discharge ring and attached to the rectifying body. The number of rectifying vanes N2 is N1 when the number of runner vanes is N1.
N2 ≧ N1
The axial-flow hydraulic machine of Claim 9 characterized by the above-mentioned. 2. The axial flow hydraulic machine according to claim 1, wherein the rectifying means is a rectifying vane provided on the discharge ring side from an intermediate position between the runner boss and the discharge ring and attached to the runner boss. The axial flow hydraulic machine according to claim 11, wherein the rectifying vanes are arranged close to a suction surface side of the runner vanes. The axial flow hydraulic machine according to claim 11, wherein a plurality of the rectifying vanes are arranged between adjacent runner vanes. The axial flow hydraulic machine according to claim 11, wherein the rectifying vane is formed shorter than the runner vane and disposed on the inlet side of the runner vane. The axial flow hydraulic machine according to claim 11, wherein the rectifying vane is disposed on an inlet side of the runner vane and protrudes outward from the inlet.

Images