JP6871879B2 - Hydraulic machine runner and hydraulic machine - Google Patents

Description

Embodiments of the present invention relate to runners of hydraulic machinery and hydraulic machinery.

In general, axial turbines such as Kaplan turbines and valve turbines used in hydroelectric power generation, and deriaz turbines such as Deriaz turbines are widely used as hydraulic machines with low head and large flow rate. These hydraulic machines are roughly classified into fixed-wing turbines and movable-wing turbines depending on whether the angle of the runner vane can be changed.

Such a hydraulic machine includes a runner and an annular stationary member provided on the outer peripheral side of the runner. The runner is rotationally driven by the water flowing through the flow path defined by the stationary member, and the generator connected to the runner generates electricity.

The runner includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. A gap is provided between the outer peripheral end surface of the runner vane and the resting member to prevent the runner vane from coming into contact with the resting member. This gap allows the runner to rotate smoothly.

However, such gaps form leak streams that do not work on the runner vanes. Therefore, there is a problem that the torque acting on the runner vane from the water flow is reduced and the efficiency of the hydraulic machine is lowered.

Japanese Unexamined Patent Publication No. 59-115475 Japanese Unexamined Patent Publication No. 60-153478

The present invention has been made in consideration of such a point, and is capable of suppressing the formation of a leak flow around the runner vane and improving the efficiency of the hydraulic machine. The purpose is to provide.

The runner of the hydraulic machine according to the embodiment is a runner of the hydraulic machine provided on the inner peripheral side of the annular stationary member. The runner of this hydraulic machine includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. The runner vanes are provided on at least one of the inner peripheral vane end face facing the outer peripheral surface of the runner boss, the outer peripheral vane end face facing the inner peripheral surface of the stationary member, and the inner peripheral vane end face and the outer peripheral vane end face. It has a vane end face groove. When the vane end face groove is provided on the inner peripheral side vane end face, the vane end face groove extends in a direction orthogonal to the flow direction of the leakage flow flowing through the gap between the outer peripheral side vane end face and the inner peripheral side vane end face, and is provided on the outer peripheral side vane end face. If so, it extends in a direction orthogonal to the flow direction of the leak flow flowing through the gap between the inner peripheral surface of the stationary member and the outer peripheral vane end surface.

Further, the runner of the hydraulic machine according to the embodiment is a runner of the hydraulic machine provided on the inner peripheral side of the annular stationary member. The runner of this hydraulic machine includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. The runner vane has an outer peripheral side vane end face facing the inner peripheral surface of the stationary member, and a vane end face groove provided on the outer peripheral side vane end face. The vane end face groove extends in a direction orthogonal to the flow direction of the leak flow flowing through the gap between the inner peripheral surface of the stationary member and the outer peripheral side vane end face.

The runner of the hydraulic machine according to the embodiment is a runner of the hydraulic machine provided on the inner peripheral side of the annular stationary member. The runner of this hydraulic machine includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. The runner vanes are provided on at least one of the inner peripheral vane end face facing the outer peripheral surface of the runner boss, the outer peripheral vane end face facing the inner peripheral surface of the stationary member, and the inner peripheral vane end face and the outer peripheral vane end face. It has an annular vane end face groove.

The runner of the hydraulic machine according to the embodiment is a runner of the hydraulic machine provided on the inner peripheral side of the annular stationary member. The runner of this hydraulic machine includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. The runner vane has an outer peripheral side vane end face facing the inner peripheral surface of the stationary member and an annular vane end face groove provided on the outer peripheral side vane end face.

The runner of the hydraulic machine according to the embodiment is a runner of the hydraulic machine provided on the inner peripheral side of the annular stationary member. The runner of this hydraulic machine includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. The runner vanes are provided on at least one of the inner peripheral vane end face facing the outer peripheral surface of the runner boss, the outer peripheral vane end face facing the inner peripheral surface of the stationary member, and the inner peripheral vane end face and the outer peripheral vane end face. It has a plurality of vane end face recesses. When the vane end face recess is provided on the inner peripheral vane end face, the maximum dimension of the vane end face recess on the inner peripheral vane end face is 3 to 6 times the dimension of the gap between the outer peripheral surface and the inner peripheral vane end face of the runner boss. When the vane end face recess is provided on the outer peripheral vane end face, the maximum dimension of the vane end face recess in the outer peripheral vane end face is 3 of the dimension of the gap between the inner peripheral surface and the outer peripheral vane end face of the stationary member. It is double to six times.

The runner of the hydraulic machine according to the embodiment is a runner of the hydraulic machine provided on the inner peripheral side of the annular stationary member. The runner of this hydraulic machine includes a runner boss and a runner vane provided on the outer peripheral side of the runner boss. The runner vane has an outer peripheral side vane end face facing the inner peripheral surface of the stationary member, and a plurality of vane end face recesses provided on the outer peripheral side vane end face. The maximum dimension of the vane end face recess on the outer peripheral side vane end face is 3 to 6 times the dimension of the gap between the inner peripheral surface of the stationary member and the outer peripheral side vane end face.

The movable impeller water turbine according to the embodiment includes the runner of the hydraulic machine described above and a stationary member provided on the outer peripheral side of the runner of the hydraulic machine.

According to the present invention, it is possible to suppress the formation of a leak flow around the runner vane and improve the efficiency of the hydraulic machine.

FIG. 1 is a cross-sectional view showing a schematic configuration of a Kaplan turbine according to the first embodiment. FIG. 2 is an enlarged cross-sectional view showing a runner and a discharge ring in the Kaplan turbine of FIG. FIG. 3 is a view of the runner of FIG. 2 as viewed from the outer peripheral side. FIG. 4 is a schematic view showing a cross section taken along the line AA of FIG. FIG. 5 is a schematic view showing a cross section taken along line BB of FIG. FIG. 6 is a diagram showing an example of a cross section taken along the line CC of FIG. FIG. 7 is a diagram showing a modified example of the cross section taken along the line CC of FIG. FIG. 8 is a diagram showing another modification of the CC line cross section of FIG. FIG. 9 is a diagram showing another modification of the CC line cross section of FIG. FIG. 10 is a view of the runner viewed from the outer peripheral side in the Kaplan turbine according to the second embodiment. FIG. 11 is a view of the runner viewed from the outer peripheral side in the Kaplan turbine according to the third embodiment. FIG. 12 is a view of the runner viewed from the outer peripheral side in the Kaplan turbine according to the fourth embodiment. FIG. 13 is a schematic view showing a cross section taken along the DD line of FIG. FIG. 14 is a schematic view showing a cross section taken along line EE of FIG. FIG. 15 is an enlarged cross-sectional view showing another example of the runner and discharge ring shown in FIG.

Hereinafter, the runner of the hydraulic machine and the hydraulic machine according to the embodiment of the present invention will be described with reference to the drawings.

(First Embodiment)
First, the runner of the hydraulic machine and the hydraulic machine according to the first embodiment will be described with reference to FIGS. 1 to 9. Here, first, a Kaplan turbine, which is an example of a hydraulic machine, will be described with reference to FIG.

As shown in FIG. 1, the Kaplan turbine 1 flows from a casing 2 into which water flows in from an upper pond (not shown), and from the casing 2 rotatably provided with respect to the casing 2 through a stay vane 3 and a guide vane 4. It includes a runner 5 that is rotationally driven by water, and a discharge ring 30 (stationary member) provided on the outer peripheral side of the runner 5.

The stay vane 3 is for forming a flow path from the casing 2 to the runner 5, and is arranged on the inner peripheral side of the casing 2. The guide vane 4 is for adjusting the flow rate of the water flowing into the runner 5, and is arranged on the inner peripheral side of the stay vane 3. By changing the opening degree of the guide vane 4, the amount of water flowing from the casing 2 into the runner 5 is adjusted, and the amount of power generation is changed.

The runner 5 is arranged on the inner peripheral side and the downstream side of the guide vane 4. The mainstream direction of the water flowing in from the casing 2 is substantially radial in the stay vane 3 and the guide vane 4, but is oriented in the direction of the runner rotation axis X (vertical direction) in the runner 5.

A generator 7 is connected to the runner 5 via a rotating spindle 6. When the runner 5 is rotationally driven by the inflowing water, power is generated in the generator 7.

A suction pipe 8 is provided on the downstream side of the runner 5. The suction pipe 8 is connected to a lower pond (not shown), and the water obtained by rotationally driving the runner 5 is discharged to the lower pond.

The discharge ring 30 described above is provided on the outer peripheral side of the runner vane 20. The discharge ring 30 is formed in an annular shape, and defines a flow path of water passing through the runner 5 provided on the inner peripheral side of the discharge ring 30.

Next, the runner 5 according to the present embodiment will be described in more detail.

As shown in FIG. 2, the runner 5 has a runner boss 10 and a plurality of runner vanes 20 provided on the outer peripheral side of the runner boss 10. Of these, the runner boss 10 is rotatable about the runner rotation axis X. The runner vanes 20 are arranged at predetermined intervals in the circumferential direction, and are provided so as to be rotatable about the vane rotation axis Y with respect to the runner boss 10. More specifically, the runner vane 20 is rotatably provided on the runner boss 10 via the spindle 15. By rotating each runner vane 20, the angle of the runner vane 20 is adjusted according to the required load (flow rate of water) and the operating head, and highly efficient operation is possible in a wide operating range. The runner boss 10 is connected to the rotary spindle 6 described above, and the rotation of the runner boss 10 is transmitted to the generator 7 via the rotary spindle 6.

The runner vane 20 has an inner peripheral vane end surface 21 facing the outer peripheral surface 11 of the runner boss 10 and an outer peripheral vane end surface 22 facing the inner peripheral surface 31 of the discharge ring 30. In FIG. 2, the inner peripheral side vane end face 21 is shown on the upstream side (upper side in FIG. 2) and the downstream side (lower side in FIG. 2) of the spindle 15.

As shown in FIG. 2, a first gap G1 is formed between the inner peripheral side vane end surface 21 and the outer peripheral surface 11 of the runner boss 10. The first gap G1 is provided to smoothly rotate the runner vane 20 with respect to the runner boss 10. Further, a second gap G2 is formed between the outer peripheral side vane end surface 22 and the inner peripheral surface 31 of the discharge ring 30. The second gap G2 is provided to smoothly rotate the runner vane 20 with respect to the runner boss 10 and smoothly rotate the runner 5 with respect to the discharge ring 30.

As shown in FIG. 3, the runner vane 20 further has a pressure surface 23 and a negative pressure surface 24 provided from the inner peripheral side vane end surface 21 to the outer peripheral side vane end surface 22. Note that FIG. 3 is a view of the runner vane 20 viewed from the outer peripheral side toward the inner peripheral side along the radial direction, and the outer peripheral side vane end surface 22 is shown on the front side, and the inner peripheral side vane end surface 22 is shown on the front side. 21 is shown.

As shown in FIGS. 2 and 3, the runner vanes 20 are provided at the vane body 25, which receives work from the water flowing into the runner 5, and the outer peripheral end of the vane body 25, which are defined by the pressure surface 23 and the negative pressure surface 24. It further has a fillet 26 provided. Of these, the fillet 26 is formed so as to project the negative pressure surface 24 of the runner vane 20 to the downstream side, and it is possible to prevent cavitation erosion from occurring on the negative pressure surface 24. The outer peripheral side vane end surface 22 is configured as a surface including the outer peripheral side end surface of the vane body 25 and the outer peripheral side end surface of the fillet 26, and the outer peripheral side end surface of the vane body 25 and the outer peripheral side end surface of the fillet 26 are continuous. It is formed smoothly.

As shown in FIG. 3, in the present embodiment, vane end face grooves 40 and 41 are provided on the inner peripheral side vane end face 21 and the outer peripheral side vane end face 22 of the runner vane 20, respectively. That is, a plurality of inner peripheral side vane end face grooves 40 are provided on the inner peripheral side vane end face 21, and a plurality of outer peripheral side vane end face grooves 41 are provided on the outer peripheral side vane end face 22.

The inner peripheral vane end face groove 40 provided on the inner peripheral vane end face 21 is orthogonal to the flow direction of the leak flow Q1 flowing through the first gap G1 between the outer peripheral surface 11 of the runner boss 10 and the inner peripheral vane end face 21. It extends in the direction of That is, the inner peripheral side vane end face groove 40 is formed in an elongated shape, and the longitudinal direction of the inner peripheral side vane end face groove 40 is a direction orthogonal to the flow direction of the leakage flow Q1. In FIG. 3, an example is shown in which the plurality of inner peripheral vane end face grooves 40 are formed in parallel with each other. The distance between the inner peripheral vane end face grooves 40 is not particularly limited, but when viewed along the radial direction, the leakage flow Q1 occurs at least once (more preferably multiple times), and the inner peripheral vane end face grooves 40. It is preferable that the interval is such that it can pass through 40.

The outer peripheral vane end face groove 41 provided on the outer peripheral side vane end face 22 is orthogonal to the flow direction of the leak flow Q2 flowing through the second gap G2 between the inner peripheral surface 31 of the discharge ring 30 and the outer peripheral side vane end face 22. It extends in the direction. That is, the outer peripheral side vane end face groove 41 is formed in an elongated shape, and the longitudinal direction of the outer peripheral side vane end face groove 41 is a direction orthogonal to the flow direction of the leakage flow Q2. In FIG. 3, an example is shown in which the plurality of outer peripheral vane end face grooves 41 are formed in parallel with each other. The distance between the outer peripheral vane end face grooves 41 is not particularly limited, but when viewed along the radial direction, the leakage flow Q2 occurs at least once (more preferably multiple times), and the outer peripheral vane end face grooves 41 are formed. It is preferable that the interval is such that it can pass through.

By the way, the runner vane 20 according to the present embodiment is rotatable with respect to the runner boss 10, and the angle of the runner vane 20 is adjusted according to a required load and an operating head. Therefore, the longitudinal direction of the vane end face grooves 40 and 41 may be defined as a direction orthogonal to the flow direction of the leakage flows Q1 and Q2 at the desired operating point. For example, it may be specified for the flow directions of the leak flows Q1 and Q2 at the design operation point and the highest efficiency operation point.

In the example shown in FIG. 3, the inner peripheral vane end face groove 40 is formed on the upstream side and the downstream side of the spindle 15 (see FIG. 2) of the inner peripheral side vane end face 21, respectively. In other words, the inner peripheral side vane end face groove 40 is formed in a region of the inner peripheral side vane end face 21 other than the region where the spindle 15 is provided. On the other hand, the outer peripheral side vane end face groove 41 is formed in the central region of the outer peripheral side vane end face 22 excluding the upstream side region and the downstream side region. However, the outer peripheral side vane end face groove 41 may be formed over the entire region of the outer peripheral side vane end face 22.

As shown in FIGS. 3 and 4, the inner peripheral vane end surface groove 40 extends from the edge of the inner peripheral vane end surface 21 on the pressure surface 23 side to the edge on the negative pressure surface 24 side. As a result, the inner peripheral side vane end face groove 40 opens at the pressure surface 23 and the negative pressure surface 24, respectively, and extends so as to penetrate the inner peripheral side vane end face 21.

As shown in FIGS. 3 and 5, the outer peripheral side vane end face groove 41 is also formed in the fillet 26 portion of the outer peripheral side vane end face 22. That is, the outer peripheral side vane end face groove 41 is formed continuously from the outer peripheral side end face of the vane body 25 to the outer peripheral side end face of the fillet 26.

The outer peripheral side vane end face groove 41 extends from the edge portion of the outer peripheral side vane end face 22 on the side of the pressure surface 23 to the edge portion on the side of the negative pressure surface 24 (in other words, the downstream side edge portion of the fillet 26). As a result, the outer peripheral side vane end face groove 41 opens at the pressure surface 23 and the negative pressure surface 24, respectively, and extends so as to penetrate the outer peripheral side vane end face 22.

The cross-sectional shape (cross-sectional shape in the direction orthogonal to the longitudinal direction) of the inner peripheral side vane end face groove 40 and the outer peripheral side vane end face groove 41 is not particularly limited. For example, as shown in FIG. 6, it may be formed in a rectangular shape. That is, in the example shown in FIG. 6, the vane end face grooves 40 and 41 are the first groove side wall 42 provided on the side of the pressure surface 23 and the first groove 24 provided on the side of the negative pressure surface 24 in a cross-sectional view. It includes a second groove side wall 43 separated from the groove side wall 42, and a groove bottom 44 extending from the first groove side wall 42 to the second groove side wall 43. The first groove side wall 42 and the second groove side wall 43 are formed perpendicularly to the vane end faces 21 and 22 and parallel to each other, and the groove bottom 44 is formed perpendicular to the first groove side wall 42 and the second groove side wall 43. Has been done.

The widths of the inner peripheral side vane end face groove 40 and the outer peripheral side vane end face groove 41 (dimensions in the direction orthogonal to the longitudinal direction) are not particularly limited, but are set according to the dimensions of the corresponding gaps G1 and G2. May be good. For example, the width w1 of the inner peripheral side vane end face groove 40 is 3 to 6 times the dimension d1 (see FIG. 2) of the first gap G1, and the width w2 of the outer peripheral side vane end face groove 41 is the second gap G2. It may be 3 to 6 times the dimension d2 (see FIG. 2) of. By making the widths w1 and w2 of the vane end face grooves 40 and 41 three times or more the dimensions d1 and d2 of the corresponding gaps G1 and G2, the water flowing into the gaps G1 and G2 is made into the vane end face grooves 40 and 41. It can be made easier to get in. On the other hand, by making the widths w1 and w2 of the vane end face grooves 40 and 41 6 times or less the dimensions d1 and d2 of the corresponding gaps G1 and G2, the flow path resistance of water passing through the gaps G1 and G2 is reduced. Can be suppressed. Further, the depth h1 of the inner peripheral side vane end face groove 40 may be about three times the dimension d1 of the first gap G1, and the depth h2 of the outer peripheral side vane end face groove 41 may be the dimension d2 of the second gap G2. It may be about 3 times as much as. Here, the dimensions d1 and d2 of the gaps G1 and G2 may be the dimensions at the operating point set when defining the longitudinal direction of the vane end face grooves 40 and 41. Further, when the dimension d1 is different at each position of the first gap G1, the minimum value may be adopted. Similarly, if the dimension d2 is different at each position of the second gap G2, the minimum value may be adopted.

Next, the operation of the present embodiment having such a configuration will be described.

During water turbine operation, as shown in FIG. 1, the water flowing into the runner 5 flows through the flow path defined by the discharge ring 30 and rotationally drives the runner 5. As a result, the runner 5 rotates and the generator 7 generates electricity.

Most of the water that has flowed into the runner 5 works on the runner vane 20 and rotationally drives the runner 5. However, as shown in FIGS. 2 and 3, some water becomes leak flows Q1 and Q2 passing through the gaps G1 and G2 around the runner vane 20 and passes through the runner vane 20 without work. More specifically, a leak flow Q1 is formed in the first gap G1 between the outer peripheral surface 11 of the runner boss 10 and the inner peripheral vane end surface 21, and the inner peripheral surface 31 of the discharge ring 30 and the outer peripheral vane end surface 22 are formed. A leak flow Q2 is formed in the second gap G2 between the two.

The water that has flowed into the first gap G1 passes through the inner peripheral side vane end face groove 40 provided on the inner peripheral side vane end face 21 before flowing out from the first gap G1. As shown in FIG. 6, the flow path of the leak flow Q1 is expanded at the position where the inner peripheral side vane end face groove 40 is provided in the first gap G1, and at the position where the inner peripheral side vane end face groove 40 is not provided. The flow path of the leak flow Q1 is narrowed and narrowed. That is, the water that has reached the position where the inner peripheral side vane end face groove 40 is provided enters the inner peripheral side vane end face groove 40 and flows in a meandering manner in the inner peripheral side vane end face groove 40. Then, the water flows out from the inner peripheral side vane end face groove 40 and flows through the narrow flow path narrowed down. In this way, a pressure loss occurs in the leak flow Q1 passing through the first gap G1. Therefore, the flow path resistance of the first gap G1 increases, and the leakage flow Q1 is weakened. In particular, in the present embodiment, since the inner peripheral side vane end face groove 40 extends in a direction orthogonal to the flow direction of the leak flow Q1, a flow along the longitudinal direction is formed in the inner peripheral side vane end face groove 40. This is suppressed, and a pressure loss is effectively generated in the leak flow Q1. Further, the pressure loss is increased by the fact that the second groove side wall 43 of the inner peripheral side vane end face groove 40 is formed perpendicular to the inner peripheral side vane end face 21.

Similarly, the water flowing into the second gap G2 passes through the outer peripheral side vane end face groove 41 provided on the outer peripheral side vane end face 22 before flowing out from the second gap G2. In the second gap G2, the flow path of the leak flow Q2 is expanded at the position where the outer peripheral side vane end face groove 41 is provided, and the flow path of the leak flow Q2 is narrowed at the position where the outer peripheral side vane end face groove 41 is not provided. Becomes narrower. That is, the water that has reached the position where the outer peripheral side vane end face groove 41 is provided enters the outer peripheral side vane end face groove 41 and flows in a meandering manner in the outer peripheral side vane end face groove 41. Then, the water flows out from the outer peripheral side vane end face groove 41 and flows through the narrow flow path narrowed down. In this way, a pressure loss occurs in the leak flow Q2 passing through the second gap G2. Therefore, the flow path resistance of the second gap G2 increases, and the leakage flow Q2 is weakened. In particular, in the present embodiment, since the outer peripheral side vane end face groove 41 extends in the direction orthogonal to the flow direction of the leak flow Q2, a flow along the longitudinal direction is formed in the outer peripheral side vane end face groove 41. This is suppressed, and a pressure loss is effectively generated in the leak flow Q2. Further, the pressure loss is increased by the fact that the second groove side wall 43 of the outer peripheral side vane end face groove 41 is formed perpendicular to the outer peripheral side vane end face 22.

As described above, according to the present embodiment, the inner peripheral side vane end face groove 40 extends in a direction orthogonal to the flow direction of the leak flow Q1 flowing through the first gap G1. As a result, a pressure loss can be effectively generated in the leak flow Q1. Therefore, the flow path resistance of the first gap G1 can be increased, and the leakage flow Q1 can be weakened. As a result, it is possible to suppress the formation of a leak flow around the runner vane 20, and it is possible to improve the efficiency of the Kaplan turbine 1.

Further, according to the present embodiment, the outer peripheral side vane end face groove 41 extends in a direction orthogonal to the flow direction of the leak flow Q2 flowing through the second gap G2. As a result, a pressure loss can be effectively generated in the leak flow Q2. Therefore, the flow path resistance of the second gap G2 can be increased, and the leakage flow Q2 can be weakened. As a result, it is possible to suppress the formation of a leak flow around the runner vane 20, and it is possible to improve the efficiency of the Kaplan turbine 1.

Further, according to the present embodiment, the outer peripheral side vane end face groove 41 is formed from the outer peripheral side vane end face 22 to the fillet 26. As a result, the pressure loss generated in the leak flow Q2 passing through the second gap G2 can be increased. Therefore, the leak flow Q2 can be further weakened.

In the above-described embodiment, an example in which the cross-sectional shapes of the vane end face grooves 40 and 41 are formed in a rectangular shape as shown in FIG. 6 has been described. However, the cross-sectional shapes of the vane end face grooves 40 and 41 are not limited to the shapes shown in FIG.

For example, as shown in FIG. 7, it may be formed in a trapezoidal shape. In the example shown in FIG. 7, the first groove side wall 42 is inclined so as to gradually become deeper toward the negative pressure surface 24 side. In this case, the water flowing through the gaps G1 and G2 can be made easier to enter through the vane end face grooves 40 and 41, and the pressure loss can be further increased.

Further, the cross-sectional shapes of the vane end face grooves 40 and 41 may be formed as shown in FIG. In the example shown in FIG. 8, the groove bottom 44 is curved so as to be recessed in the deepening direction (right side in FIG. 8). Also in this case, the water flowing through the gaps G1 and G2 can be made easier to enter through the vane end face grooves 40 and 41, and the pressure loss can be further increased.

Further, the cross-sectional shapes of the vane end face grooves 40 and 41 may be formed as shown in FIG. In the example shown in FIG. 9, the groove bottom 44 is curved so as to be recessed in the deepening direction (right side in FIG. 9), and the first groove side wall 42 and the second groove side wall 43 are inclined. The first groove side wall 42 and the second groove side wall 43 are inclined so as to gradually become deeper toward the negative pressure surface 24 side. Also in this case, the water flowing through the gaps G1 and G2 can be made easier to enter through the vane end face grooves 40 and 41, and the pressure loss can be further increased.

Further, in the above-described embodiment, the inner peripheral vane end face 21 of the runner vane 20 is provided with the inner peripheral vane end face groove 40, and the outer peripheral vane end face 22 is provided with the outer peripheral vane end face groove 41. I explained the example. However, the present invention is not limited to this, and even if the outer peripheral side vane end face 22 is not provided with the outer peripheral side vane end face groove 41, the inner peripheral side vane end face groove 40 passes through the first gap G1. It is possible to effectively cause a pressure loss in the leak flow Q1. Similarly, even when the inner peripheral side vane end face 21 is not provided with the inner peripheral side vane end face groove 40, the outer peripheral side vane end face groove 41 is effective for the leak flow Q2 passing through the second gap G2. Can cause pressure loss.

Further, in the above-described embodiment, an example in which the fillet 26 is provided at the outer peripheral side end of the negative pressure surface 24 of the runner vane 20 has been described. However, such a fillet 26 may not be provided.

(Second Embodiment)
Next, the runner of the hydraulic machine and the hydraulic machine according to the second embodiment of the present invention will be described with reference to FIG.

In the second embodiment shown in FIG. 10, between the end of each vane end face groove on the pressure surface side and the pressure surface, and between the end of each vane end face groove on the negative pressure surface side and the negative pressure surface. The main difference is that groove end walls are provided between them, and the other configurations are substantially the same as those of the first embodiment shown in FIGS. 1 to 9. In FIG. 10, the same parts as those in the first embodiment shown in FIGS. 1 to 9 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the present embodiment, as shown in FIG. 10, the inner peripheral side groove end wall 50 is provided between the end portion of the inner peripheral side vane end surface groove 40 on the pressure surface 23 side and the pressure surface 23. .. Further, an inner peripheral side groove end wall 50 is also provided between the end portion of the inner peripheral side vane end surface groove 40 on the negative pressure surface 24 side and the negative pressure surface 24. As a result, the inner peripheral vane end face groove 40 is not open on either the pressure surface 23 or the negative pressure surface 24, and does not penetrate the inner peripheral side vane end face 21.

Similarly, the outer peripheral side groove end wall 51 is provided between the end portion of the outer peripheral side vane end surface groove 41 on the pressure surface side side and the pressure surface 23. Further, the outer peripheral side groove end wall 51 is also provided between the end portion of the outer peripheral side vane end surface groove 41 on the negative pressure surface 24 side and the negative pressure surface 24. As a result, the outer peripheral side vane end face groove 41 is not open on either the pressure surface 23 or the negative pressure surface 24, and does not penetrate the outer peripheral side vane end face 22.

As described above, according to the present embodiment, between the end portion of the inner peripheral side vane end face groove 40 on the pressure surface 23 side and the pressure surface 23, and on the side of the negative pressure surface 24 of the inner peripheral side vane end face groove 40. An inner peripheral side groove end wall 50 is provided between the end portion and the negative pressure surface 24, respectively. This makes it possible to prevent the formation of a flow of water flowing in the longitudinal direction of the inner peripheral side vane end face groove 40. Therefore, the leak flow Q1 flowing through the first gap G1 can be further weakened. As a result, the formation of a leak flow around the runner vane 20 can be further suppressed, and the efficiency of the Kaplan turbine 1 can be further improved.

Further, according to the present embodiment, between the end portion of the outer peripheral side vane end surface groove 41 on the pressure surface 23 side and the pressure surface 23, and the end portion of the outer peripheral side vane end surface groove 41 on the negative pressure surface 24 side. An outer peripheral side groove end wall 51 is provided between the negative pressure surface 24 and the outer peripheral side groove end wall 51, respectively. This makes it possible to prevent the formation of a flow of water flowing in the longitudinal direction of the outer peripheral side vane end face groove 41. Therefore, the leak flow Q2 flowing through the second gap G2 can be further weakened. As a result, the formation of a leak flow around the runner vane 20 can be further suppressed, and the efficiency of the Kaplan turbine 1 can be further improved.

In the present embodiment described above, between the end of the inner peripheral side vane end surface groove 40 on the pressure surface 23 side and the pressure surface 23, and on the side of the negative pressure surface 24 of the inner peripheral side vane end surface groove 40. An example in which the inner peripheral side groove end wall 50 is provided between the end portion and the negative pressure surface 24 has been described. However, the present invention is not limited to this, and the space between the end of the inner peripheral vane end face groove 40 on the pressure surface 23 side and the pressure surface 23, and the side of the inner peripheral side vane end face groove 40 on the negative pressure surface 24 side. The inner peripheral side groove end wall 50 may not be provided on either one of the end portion and the negative pressure surface 24. Even in this case, the leak flow Q1 flowing through the first gap G1 can be weakened. Similarly, between the end of the outer peripheral vane end surface groove 41 on the pressure surface side side and the pressure surface 23, and between the end of the outer peripheral side vane end surface groove 41 on the negative pressure surface 24 side and the negative pressure surface 24. The outer peripheral side groove end wall 51 may not be provided on either one.

(Third Embodiment)
Next, the runner of the hydraulic machine and the hydraulic machine according to the third embodiment of the present invention will be described with reference to FIG.

The third embodiment shown in FIG. 11 is mainly different in that the vane end face groove is formed in an annular shape, and the other configurations are substantially the same as those of the first embodiment shown in FIGS. 1 to 9. Is. In FIG. 11, the same parts as those in the first embodiment shown in FIGS. 1 to 9 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the present embodiment, as shown in FIG. 11, the inner peripheral side vane end face groove 40 and the outer peripheral side vane end face groove 41 are each formed in an annular shape when viewed along the radial direction. In the example shown in FIG. 11, the vane end face grooves 40 and 41 are formed in an annular shape.

The inner peripheral side vane end face groove 40 is not open on either the pressure surface 23 or the negative pressure surface 24, and does not penetrate the inner peripheral side vane end face 21. That is, the inner peripheral side groove side wall 60 is provided between the inner peripheral side vane end surface groove 40 and the pressure surface 23, and between the inner peripheral side vane end surface groove 40 and the negative pressure surface 24, respectively.

Similarly, the outer peripheral side vane end face groove 41 is not open on either the pressure surface 23 or the negative pressure surface 24, and does not penetrate the outer peripheral side vane end face 22. That is, the outer peripheral side groove side wall 61 is provided between the outer peripheral side vane end surface groove 41 and the pressure surface 23, and between the outer peripheral side vane end surface groove 41 and the negative pressure surface 24, respectively.

Further, as shown in FIG. 11, the outer peripheral side vane end face groove 41 is also formed in the fillet 26 portion of the outer peripheral side vane end face 22. That is, the outer peripheral side vane end face groove 41 is formed continuously from the outer peripheral side end face of the vane body 25 to the outer peripheral side end face of the fillet 26.

In the example shown in FIG. 11, the plurality of outer peripheral vane end surface grooves 41 are arranged in a row in the direction along the pressure surface 23 or the negative pressure surface 24 when viewed along the radial direction. However, the arrangement is not limited to this, and the arrangement of the outer peripheral side vane end face groove 41 is arbitrary as long as the leakage flow Q2 passing through the second gap G2 can pass through the outer peripheral side vane end face groove 41 at least once. Is. The same applies to the inner peripheral side vane end face groove 40, but in FIG. 11, an example in which one inner peripheral side vane end face groove 40 is provided on the upstream side and the downstream side of the spindle 15 (see FIG. 2). It is shown.

As described above, according to the present embodiment, the inner peripheral side vane end face groove 40 is formed in an annular shape. As a result, the water that has flowed into the inner peripheral side vane end face groove 40 can circulate in the inner peripheral side vane end face groove 40. Therefore, the flow path resistance of the first gap G1 can be increased, and the leak flow Q1 flowing through the first gap G1 can be further weakened. In particular, according to the present embodiment, since the inner peripheral side vane end face groove 40 is formed in an annular shape, the water in the inner peripheral side vane end face groove 40 can be smoothly circulated, and the first gap can be circulated smoothly. The flow path resistance of G1 can be further increased.

Further, according to the present embodiment, the outer peripheral side vane end face groove 41 is formed in an annular shape. As a result, the water that has flowed into the outer peripheral side vane end face groove 41 can circulate in the outer peripheral side vane end face groove 41. Therefore, the flow path resistance of the second gap G2 can be increased, and the leak flow Q2 flowing through the second gap G2 can be further weakened. In particular, according to the present embodiment, since the outer peripheral side vane end face groove 41 is formed in an annular shape, the water in the outer peripheral side vane end face groove 41 can be smoothly circulated, and the second gap G2 The flow path resistance can be further increased.

Further, according to the present embodiment, the inner peripheral side vane end face groove 40 is formed in an annular shape. As a result, it is possible to prevent the effect of causing a pressure loss in the leak flow Q1 from depending on the flow direction of the leak flow Q1 passing through the first gap G1, and it depends on the operating point (angle of the runner vane 20). Can be prevented. Similarly, since the outer peripheral side vane end face groove 41 is formed in an annular shape, it is possible to prevent the effect of causing a pressure loss in the leakage flow Q2 passing through the second gap G2 from depending on the operating point.

(Fourth Embodiment)
Next, the runner of the hydraulic machine and the hydraulic machine according to the fourth embodiment of the present invention will be described with reference to FIGS. 12 to 14.

The fourth embodiment shown in FIGS. 12 to 14 is mainly different in that each vane end face is provided with a vane end face recess, and the other configurations are the first embodiment shown in FIGS. 1 to 9. It is almost the same as the form of. In FIGS. 12 to 14, the same parts as those in the first embodiment shown in FIGS. 1 to 9 are designated by the same reference numerals, and detailed description thereof will be omitted.

In the present embodiment, as shown in FIG. 12, the inner peripheral side vane end face 21 is provided with the inner peripheral side vane end face recess 70. In the present embodiment, the inner peripheral side vane end face recess 70 is formed in a circular shape when viewed along the radial direction.

The maximum dimension of the inner peripheral vane end face recess 70 in the inner peripheral vane end face 21 (diameter of the inner peripheral vane end face recess 70 in the present embodiment) is three times the dimension d1 (see FIG. 2) of the first gap G1. It is ~ 6 times. By making the maximum dimension of the inner peripheral side vane end face recess 70 three times or more the dimension d1 of the first gap G1, it is possible to make it easier for the water flowing into the first gap G1 to enter the inner peripheral side vane end face recess 70. it can. On the other hand, by making the maximum dimension of the inner peripheral side vane end face recess 70 6 times or less the dimension d1 of the first gap G1, it is possible to suppress the loss of the effect of increasing the flow path resistance of the first gap G1. The inner peripheral side vane end face groove 40 is not limited to being formed in a circular shape, but may be formed in a polygonal shape such as a rectangular shape or a hexagonal shape. For example, when the inner peripheral side vane end face groove 40 is formed in a rectangular shape or a hexagonal shape, the maximum dimension of the inner peripheral side vane end face groove 40 corresponds to the longest diagonal length.

Further, the outer peripheral side vane end face 22 is provided with the outer peripheral side vane end face recess 71. In the present embodiment, the outer peripheral side vane end face recess 71 is formed in a circular shape when viewed along the radial direction.

The maximum dimension of the outer peripheral vane end face recess 71 on the outer peripheral vane end face 22 (diameter of the outer peripheral vane end face recess 71 in the present embodiment) is 3 to 6 times the dimension d2 (see FIG. 2) of the second gap G2. It has become. By making the maximum dimension of the outer peripheral side vane end face recess 71 three times or more the dimension d2 of the second gap G2, it is possible to facilitate the water flowing into the second gap G2 to enter the outer peripheral side vane end face recess 71. On the other hand, by making the maximum dimension of the outer peripheral side vane end face recess 71 6 times or less the dimension d2 of the second gap G2, it is possible to suppress the loss of the effect of increasing the flow path resistance of the second gap G2. The outer peripheral side vane end face groove 41 is not limited to being formed in a circular shape as in the inner peripheral side vane end face groove 40, and is arbitrary.

Further, when viewed along the radial direction, the inner peripheral side vane end face recesses 70 may be arranged regularly or randomly, which is arbitrary. In the example shown in FIG. 12, the inner peripheral side vane end face recess 70 is formed on the upstream side and the downstream side of the spindle 15 (see FIG. 2) of the inner peripheral side vane end face 21, respectively.

When viewed along the radial direction, the outer peripheral vane end face recesses 71 may be arranged regularly or randomly, which is arbitrary. In the example shown in FIG. 12, the outer peripheral side vane end face recess 71 is formed in the central region of the outer peripheral side vane end face 22 excluding the upstream side region and the downstream side region. However, the outer peripheral side vane end face recess 71 may be formed over the entire region of the outer peripheral side vane end face 22. Further, the outer peripheral side vane end face recess 71 is also formed in the portion of the fillet 26. That is, the outer peripheral side vane end face recess 71 is formed on the outer peripheral side end face of the vane body 25 and the outer peripheral side end face of the fillet 26, respectively.

The cross-sectional shape of the inner peripheral side vane end face recess 70 and the outer peripheral side vane end face recess 71 is not particularly limited. For example, as shown in FIG. 13, it may be formed in a trapezoidal shape. The depth h3 of the inner peripheral side vane end face recess 70 may be about three times the dimension d1 of the first gap G1, and the depth h4 of the outer peripheral side vane end face recess 71 may be 3 of the dimension d2 of the second gap G2. It may be doubled.

During operation of the water turbine, the water that has flowed into the first gap G1 passes through the inner peripheral side vane end face recess 70 provided in the inner peripheral side vane end face 21 before flowing out from the first gap G1. The flow path of the leak flow Q1 is expanded at the position where the inner peripheral side vane end face recess 70 is provided in the first gap G1, and the flow path of the leak flow Q1 is expanded at the position where the inner peripheral side vane end face recess 70 is not provided. It is squeezed and narrowed. That is, the water that has reached the position where the inner peripheral side vane end face recess 70 is provided enters the inner peripheral side vane end face recess 70 and flows in a meandering manner in the inner peripheral side vane end face recess 70. Then, the water flows out from the inner peripheral side vane end face recess 70 and flows through the narrow flow path narrowed down. In this way, a pressure loss occurs in the leak flow Q1 passing through the first gap G1. Therefore, the flow path resistance of the first gap G1 increases, and the leakage flow Q1 is weakened.

Similarly, the water flowing into the second gap G2 passes through the outer peripheral side vane end face recess 71 provided on the outer peripheral side vane end face 22 before flowing out from the second gap G2. The flow path of the leak flow Q2 is expanded at the position of the second gap G2 where the outer peripheral side vane end face recess 71 is provided, and the flow path of the leak flow Q2 is narrowed at the position where the outer peripheral side vane end face recess 71 is not provided. Becomes narrower. That is, the water that has reached the position where the outer peripheral side vane end face recess 71 is provided enters the outer peripheral side vane end face recess 71 and flows in a meandering manner in the outer peripheral side vane end face recess 71. Then, the water flows out from the outer peripheral side vane end face recess 71 and flows through the narrow flow path narrowed down. In this way, a pressure loss occurs in the leak flow Q2 passing through the second gap G2. Therefore, the flow path resistance of the second gap G2 increases, and the leakage flow Q2 is weakened.

As described above, according to the present embodiment, the inner peripheral side vane end face recess 70 is provided on the inner peripheral side vane end face 21. As a result, a pressure loss can be effectively generated in the leak flow Q1 passing through the first gap G1. Therefore, the flow path resistance of the first gap G1 can be increased, and the leakage flow Q1 can be weakened. As a result, it is possible to suppress the formation of a leak flow around the runner vane 20, and it is possible to improve the efficiency of the Kaplan turbine 1.

Further, according to the present embodiment, the maximum dimension of the inner peripheral side vane end face recess 70 in the inner peripheral side vane end face 21 is 3 to 6 times the dimension d1 of the first gap G1. As a result, a large number of inner peripheral side vane end face recesses 70 can be formed on the inner peripheral side vane end face 21. Therefore, the number of times the leak flow Q1 passing through the first gap G1 passes through the inner peripheral side vane end face recess 70 can be increased, and the flow path resistance of the first gap G1 can be further increased.

Further, according to the present embodiment, the outer peripheral side vane end face 22 is provided with the outer peripheral side vane end face recess 71. As a result, a pressure loss can be effectively generated in the leak flow Q2 passing through the second gap G2. Therefore, the flow path resistance of the second gap G2 can be increased, and the leakage flow Q2 can be weakened. As a result, it is possible to suppress the formation of a leak flow around the runner vane 20, and it is possible to improve the efficiency of the Kaplan turbine 1.

Further, according to the present embodiment, the maximum dimension of the outer peripheral side vane end face recess 71 on the outer peripheral side vane end face 22 is 3 to 6 times the dimension d2 of the second gap G2. As a result, a large number of outer peripheral vane end face recesses 71 can be formed on the outer peripheral side vane end face 22. Therefore, the number of times the leak flow Q2 passing through the second gap G2 passes through the outer peripheral side vane end face recess 71 can be increased, and the flow path resistance of the second gap G2 can be further increased.

Further, according to the present embodiment, the inner peripheral side vane end face recess 70 is formed in a circular shape. As a result, it is possible to prevent the effect of causing a pressure loss in the leak flow Q1 from depending on the flow direction of the leak flow Q1 passing through the first gap G1, and it depends on the operating point ((angle of runner vane 20)). Similarly, since the outer peripheral side vane end face recess 71 is formed in a circular shape, the effect of causing a pressure loss in the leak flow Q2 passing through the second gap G2 depends on the operating point. Can be prevented.

According to the above-described embodiment, it is possible to suppress the formation of a leak flow around the runner vane and improve the efficiency of the hydraulic machine.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the gist of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof. Further, as a matter of course, it is also possible to partially and appropriately combine these embodiments within the scope of the gist of the present invention.

In each of the above-described embodiments, the Kaplan turbine 1 has been described as an example of a hydraulic machine in which the runner vane 20 is rotatable with respect to the runner boss 10. However, the present invention is not limited to this, and each embodiment can be applied to turbines other than Kaplan turbine 1. Further, if the runner 5 and the annular stationary member such as the discharge ring 30 are provided, the turbine can be applied to an axial turbine such as a valve turbine and a deriaz turbine such as a deriaz turbine. For example, as shown in FIG. 15, the runner vane 20 may be non-rotatably fixed to the runner boss 10. In this case, since the runner vane 20 is integrated with the runner boss 10, the first gap G1 does not exist. When the runner vane 20 is fixed so as not to be rotatable in this way, by providing the outer peripheral side vane end face groove 41 on the outer peripheral side vane end face 22, the pressure is effectively applied to the leak flow Q2 passing through the second gap G2. Loss can occur. Furthermore, each embodiment can also be applied to a water turbine that can be operated by a pump.

1: Kaplan turbine, 5: runner, 10: runna boss, 11: outer peripheral surface, 20: runner vane, 21: inner peripheral side vane end face, 22: outer peripheral side vane end face, 23: pressure surface, 24: negative pressure surface, 25: vane Main body, 26: Fillet, 30: Discharge ring, 31: Inner peripheral surface, 40: Inner peripheral side vane end face groove, 41: Outer peripheral side vane end face groove, 50: Inner peripheral side groove end wall, 51: Outer peripheral side groove end wall, 70 : Inner peripheral vane end face recess, 71: Outer peripheral vane end face recess, G1: 1st gap, G2: 2nd gap, Q1, Q2: Leakage flow,

Claims (3)

It is a runner of a hydraulic machine provided on the inner peripheral side of an annular stationary member.
With Lanna Boss
With a runner vane provided on the outer peripheral side of the runner boss,
The runner vane is a runner of a hydraulic machine having an outer peripheral side vane end face facing the inner peripheral surface of the stationary member and an annular vane end face groove provided on the outer peripheral side vane end face. The runner of the hydraulic machine according to claim 1 , wherein the vane end face groove is formed in an annular shape. The runner of the hydraulic machine according to claim 1 or 2,
A hydraulic machine including the stationary member provided on the outer peripheral side of the runner of the hydraulic machine.

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