JP5831877B2 - Fluidic rotating machine testing apparatus and fluid rotating machine testing method - Google Patents

Description

  The present invention relates to a test apparatus for a fluid-type rotating machine for testing the characteristics of a fluid-type rotating machine such as a windmill that rotates by generating torque by a fluid force.

  2. Description of the Related Art Conventionally, a large number of fluid-type rotating machines that perform rotation by taking out a fluid force of water or air to generate a rotational torque are known. For example, there are water turbines and wind turbines used for power generation, and these are attracting attention as clean power generation means using natural energy. The same applies to steam turbines and gas turbines in that the rotational torque is extracted from the fluid force.

  In such a fluid rotating machine, a plurality of blades and fins as torque generating portions are attached to a rotating shaft that is rotatably supported, and rotational torque is generated when fluid acts on these blades and fins. In common.

  The above-mentioned fluid rotating machine can be classified in various ways. First, it can be roughly classified according to the direction in which the rotating shaft is arranged with respect to the fluid flow direction. For example, wind turbines generally used as wind power generators are roughly classified into vertical axis type wind turbines and horizontal axis type wind turbines. Further, it is possible to classify by the principle of generation of torque by the fluid. For example, wind turbines are generally divided into a drag type and a lift type. Furthermore, it is further classified according to the shape of wings and fins.

  Here, the thing of patent document 1 is disclosed as a lift type electric power generating apparatus provided with the vertical axis type windmill which arrange | positions a some straight blade | wing. This is based on a configuration in which a shaft connected to a generator is rotatably installed with its longitudinal direction set to a vertical direction, and a plurality of blades are arranged in the circumferential direction with respect to this shaft, and the blades are more than conventional. The purpose is to improve the power generation efficiency by changing the surface shape. As described above, various techniques have been proposed and improved in order to extract energy more efficiently than fluid.

Japanese Patent No. 4151940

  However, there is a need in the market to achieve higher energy efficiency and there is a need for further improvements.

  For this reason, technological development has been advanced on the basis of numerical analysis to optimize various elements such as the shape, positional relationship with the rotation axis, installation conditions and number of blades and fins, and so on. A certain effect is being obtained along with the improvement in the performance of computers used in the system.

  Since numerical analysis is generally performed by simplifying the model, even in a hydraulic rotating machine having a plurality of blades or fins, a method of modeling a single blade or fin and analyzing the rotational torque obtained by the force generated in the fluid is used. Often taken. In this case, it is possible to predict the force acting on the entire hydrodynamic rotating machine by adding the rotational torques generated in the individual blades.

  However, at present, it is difficult to say that all the phenomena that occur in a fluid-type rotating machine can be simulated by such numerical analysis alone, and it can be said that verification experiments using actual machines are still indispensable.

  Specifically, for wings and fins in a fluid-type rotating machine, even if it is possible to analyze the drag and lift generated inside a fluid moving at a constant speed, torque is generated and rotated with the rotating shaft every moment. Considering the situation where the relative speed changes, it becomes difficult to perform an accurate analysis. In addition, since the conditions of the apparatus constantly change as the blades and fins are deformed by the resistance and centrifugal force received from the fluid, the actual phenomenon becomes more complicated and difficult to analyze. Furthermore, it is conceivable that the wings and fins adversely affect the flow of the fluid to create an irregular flow, which further complicates the phenomenon and makes the analysis difficult.

  Also, numerical analysis may be more difficult depending on the type of fluid rotary machine. For example, considering the case of a vertical axis type windmill as in Patent Document 1, the characteristics of the windmill as a whole include a number of parameters such as wind receiving area, rotational radius, blade shape, number of blades, chord length, blade attachment angle, and the like. Numerical analysis for optimization purposes is extremely complicated. In addition, since the wing always changes direction with respect to the wind, the direction in which lift and drag are generated changes. That is, the rotational torque varies greatly during one rotation. Furthermore, when there are a plurality of blades, the positional relationship between the blades is switched between the upstream side and the downstream side during rotation. Therefore, when considering the torque generated by one blade, the influence of the other blades through the fluid flow It is necessary to consider even receiving. Therefore, it can be said that it is difficult to perform numerical simulation to accurately reproduce the actual phenomenon, and it is necessary to use it together with the verification experiment.

  As a verification experiment, it is easy to perform a torque measurement by attaching a torque meter to the rotating shaft of a fluid-type rotating machine. Based on the data obtained in this way, the validity of the numerical analysis results is confirmed and the accuracy of the analysis is verified. Improvements are being made.

  However, such means can only measure the total torque obtained from a plurality of blades and fins, and as described above, it is not possible to examine in detail the appropriateness of the torque generated by a single blade or fin determined by numerical analysis. Can not. Therefore, it cannot be said that it is truly useful for examining the optimum shape and optimum installation conditions for the wings and fins as the torque generating part.

  In view of the above-described problems, an object of the present invention is to provide a test apparatus for a fluid-type rotating machine that can accurately measure torque generated by a single torque generator.

  In order to achieve this object, the present invention takes the following measures.

  That is, the fluid rotating machine testing apparatus of the present invention includes a rotating shaft that is rotatably supported, and a torque generating unit that generates torque to be transmitted to the rotating shaft by a fluid flow. One torque generating unit is configured as a torque measurement target unit so as to be rotatable relative to the rotation shaft, and a torque detector is provided between the rotation shaft and the torque measurement target unit.

  With this configuration, the torque generated by the torque generating unit alone can be accurately measured, so that the torque generated by the fluid rotary machine can be investigated in more detail. Therefore, it is possible to strictly verify the results of numerical analysis based on actual phenomena, and as an effective tool for realizing a more efficient fluid rotary machine by optimizing the torque generator It can be used.

  In addition, the configuration for obtaining the above-described effects is configured in a simple and practical manner, and the characteristics of the fluid-type rotating machine as a whole are maintained, and a test in a state closer to an actual fluid-type rotating machine is performed. In order to make it possible, an integral rotating portion that rotates integrally with the rotating shaft, and a relative rotating portion that is rotatable integrally with the torque measurement target portion and relatively rotatable with respect to the rotating shaft, It is preferable that the integral rotation unit and the relative rotation unit are arranged to face each other and that the integral rotation unit and the relative rotation unit are connected via the torque detector.

  Further, in the fluid rotating machine in which the torque generating unit changes its positional relationship between the upstream side and the downstream side with respect to the rotating shaft when the rotating shaft of the torque generating unit is perpendicular to the fluid flow. In order to make it possible to investigate characteristic torque fluctuations in detail by an experimental method, the rotating shaft may be arranged in a direction perpendicular to the fluid flow direction. Is preferred.

  Further, even when the rotation plane of the torque generating unit is perpendicular to the flow of the fluid, in order to make it possible to investigate the torque fluctuation characteristic of this in detail by an experimental method, It is preferable that the rotating shaft is arranged in a direction parallel to the fluid flow direction.

  Further, in order to effectively use as a tool for improving the efficiency of a windmill widely used in wind power generation or the like, it is preferable that the fluid is air and the fluid rotating machine is configured as a windmill. Is,

  Furthermore, the fluid rotary machine testing method of the present invention uses any one of the fluid rotary machine testing devices described above to detect the torque transmitted to the rotating shaft by the torque measurement target unit, and to detect the detected torque. By treating the torque generated in the torque generating unit alone, the characteristic evaluation of the torque generating unit is performed.

  By doing so, the detected torque obtained is used as a torque generated in the torque generating unit alone, and the result of matching with the numerical analysis results separately performed focusing on the individual torque generating units, the optimal shape as the torque generating unit It is possible to search for installation conditions and realize a more efficient fluid rotary machine.

  According to the present invention described above, the torque generated by a single torque generator can be measured, and the torque generated by the fluid rotating machine can be investigated in more detail, and a highly efficient fluid rotating machine can be realized. It is possible to provide a test apparatus for a fluid-type rotating machine that can be effectively used as a tool for the above.

1 is a perspective view of a test apparatus for a fluid rotary machine according to a first embodiment of the present invention. The system block diagram of the testing apparatus of the fluid rotary machine. The partial cross-section enlarged view of the testing apparatus of the fluid rotary machine. The XX cross-section arrow enlarged view in FIG. Explanatory drawing which shows the calculation method of the torque in the testing apparatus of the fluid rotary machine. Explanatory drawing which shows the relationship between the rotation angle of a wing | blade and the mainstream direction of a wind in the testing apparatus of the fluid rotary machine. Explanatory drawing which shows the general parameter used as the installation reference | standard of a wing | blade. Explanatory drawing which shows an example of the data which can be obtained using the testing apparatus of the fluid rotary machine. The fragmentary sectional view of the testing apparatus of the fluid rotary machine concerning a 2nd embodiment of the present invention. The fragmentary sectional view which shows the example which deform | transformed 1st Embodiment of this invention.

Embodiments of the present invention will be described below with reference to the drawings.
<First Embodiment>

  As shown in FIG. 1, the fluid rotating machine testing apparatus of this embodiment is configured as a vertical axis wind turbine testing apparatus 1. Therefore, the whole is standing upright in the vertical direction, and the rotating shaft 2 is arranged perpendicular to the main flow direction (W direction in the drawing) of the wind (air) as the fluid flow direction.

  The vertical axis wind turbine is generally connected to a generator to generate power, and is used for the purpose of converting wind energy into mechanical energy and then converting it into electrical energy. Therefore, it can be said that it is necessary to convert wind energy into mechanical energy with higher efficiency, that is, to obtain a larger torque through the rotating shaft 2. It can also be said that it is important to obtain a stable torque in any wind condition. The vertical axis wind turbine test apparatus 1 according to the present embodiment is intended for a performance test as a single vertical axis wind turbine, but is similar to a general power generator having a vertical axis wind turbine as follows. It is the composition to do.

  The rotating shaft 2 is rotatably supported by the frame 11 and can control the rotation speed by a motor 57 provided below. In addition, two torque generators 3A and 3B are provided for generating torque to be transmitted to the rotating shaft 2. Among these, one torque generating unit 3A is directly fixed to the rotating shaft 2 via another member to transmit torque directly to the rotating shaft 2, and the other torque generating unit 3B is a torque described later. A torque is indirectly transmitted to the rotating shaft 2 via a detector. That is, in the present embodiment, the torque generator 3A is configured as a torque measurement non-target part, and the torque generator 3B is configured as a torque measurement target part.

  The torque generator 3A is mainly composed of a linear wing 41 arranged substantially parallel to the rotary shaft 2 and a pair of support arms 42, 42 formed in a linear shape. As a result, torque in the rotational direction is generated. Specifically, lift and drag are generated in the wing 41 by the wind, and torque obtained by multiplying the rotational direction component of the resultant force of the lift and drag by the length of the support arms 42 and 42 is applied to the rotating shaft 2. I am doing so. The torque generator 3B has the same configuration, and is mainly composed of a linear wing 41 arranged substantially parallel to the rotary shaft 2 and a pair of support arms 43, 43 formed in a step shape. The wings 41 and 41 are arranged at symmetrical positions around the rotation axis 2 and rotate while sharing the same rotation locus.

  Hereinafter, the detailed configuration will be described with reference to other drawings. FIG. 2 is a side view of the test apparatus 1 for a vertical axis wind turbine according to the present embodiment, and a part thereof is represented as a vertical sectional view. Further, the system configuration diagram showing the relationship with the control unit 7 is also shown.

  The frame 11 has a three-story structure including a first frame 11a, a second frame 11b fixed on the first frame 11a, and a support portion 12 as a third frame. The first frame 11a is composed of an angle member standing upright and arranged on four sides and combined with a bottom plate and a top plate to form a rectangular parallelepiped shape. The second frame 11b also has a rod-like member standing upright on the first frame 11a. It is arranged in a circle and has a top plate on it.

  Furthermore, the support part 12 fixed on the 2nd flame | frame 11b is formed as a cylindrical member, and supports the rotating shaft 2 with the bearing provided in this inside. Specifically, the bearing 13 and another bearing (not shown) are arranged in the support portion 12 so as to be vertically separated from each other so that the rotary shaft 2 is supported rotatably. Further, by using a thrust bearing in addition to the radial bearing, the weight of the rotary shaft 2 can be appropriately supported from below.

  In addition, a rotation detector 53 for detecting the rotation phase angle and the rotation speed of the rotating shaft 2 is provided inside the support portion 12. The rotation detector 53 includes a slit plate 53a attached to the rotating shaft 2 as a unit, and a photoelectric sensor 53b including a light projecting element and a light receiving element disposed so as to sandwich the slit plate 53a. In response to this, a pulse signal is output.

  In addition, a slip ring 55 is provided on the rotary shaft 2 inside the support portion 12, and an electric cable is passed between a cable (not shown) passing through the hollow hole 2 a provided on the rotary shaft 2 and an external device. Signals can be exchanged.

  Inside the second frame 11b, a brake unit 54 for applying a braking torque to the rotating shaft 2 is provided. By applying an electric signal from the outside to the brake unit 54, it is possible to apply a braking torque to the rotating shaft 2 at an arbitrary timing.

  Further, a torque converter 52 is provided at the lower end of the rotating shaft 2 via a shaft joint, and a motor 57 is provided below the torque converter 52 via another shaft joint. The torque converter 52 can detect the amount of twist of the internal shaft, convert it into torque, and output it. By doing so, it is possible to apply an electrical signal to the motor 57 to rotate the rotary shaft 2 at an arbitrary speed and to detect the torque transmitted to the motor 57 from the rotary shaft 2 side. Yes.

  The motor 57 can also be used as a regenerative brake. When the rotating shaft 2 does not reach the target speed only with the torque generated by the torque generating units 3A and 3B, the rotating torque is applied by the motor 57 to rotate the rotating shaft. When 2 is going to rotate beyond the target speed, it can be adjusted to the target speed by applying a braking torque.

  As described above, the torque generator 3A, which is a torque measurement non-target part, mainly includes the blade 41 and the pair of support arms 42, 42, and the torque generator 3B, which is a torque measurement target part, mainly includes the blade 41. And a pair of support arms 43, 43. Each of the support arms 42 to 43 is provided so as to extend in a direction orthogonal to the axial direction of the rotary shaft 2, and each tip has a fastening means such as a screw with respect to a stay 41 s provided on the wing 41. (Not shown).

  Connections between the support arms 42 to 43 and the rotary shaft 2 are made as shown in the enlarged sectional view of FIG.

  First, a fixed disk 21 that is orthogonal to the axial direction of the rotating shaft 2 and is coaxially disposed is provided on the upper portion of the rotating shaft 2, together with a support member 21 a that is attached to the rotating shaft 2 using a key. The rotary shaft 2 and the rotary shaft 2 are rotated together. Further, a fixed disk 22 is provided in parallel to the fixed disk 21 and at a predetermined distance below. Similarly to the fixed disk 21, this is arranged coaxially with the rotary shaft 2 and rotates together with the rotary shaft 2 together with a support member 22a attached to the rotary shaft 2 using a key. Further, with respect to the fixed disks 21 and 22, the linear support arms 42 and 42 are perpendicular to the axial direction of the rotary shaft 2 and are parallel to each other using fastening means such as screws. Each is fixed.

  In addition, two non-fixed disks 23 and 24 are provided between the two fixed disks 21 and 22. The non-fixed disk 23 is provided immediately below the fixed disk 21, and similarly to this, it is orthogonal to the axial direction of the rotating shaft 2 and is arranged coaxially. Then, the non-fixed disk 23 is restricted only in the axial direction with respect to the rotary shaft 2 by being fixed to the support member 23 a provided rotatably with respect to the rotary shaft 2 via the bearing 25. The rotation direction is non-fixed so that it can rotate relative to the same axis. Further, the non-fixed disk 24 is provided immediately above the fixed disk 22, and similarly to this, it is orthogonal to the axial direction of the rotary shaft 2 and is arranged coaxially. Then, like the non-fixed disk 23, the non-fixed disk 24 is fixed to the rotary shaft 2 by being fixed to a support member 24 a that is rotatably provided to the rotary shaft 2 via a bearing 25. While the position is restricted only in the axial direction, it is not fixed in the rotational direction and can rotate relative to the same axis.

  Further, with respect to the non-fixed disks 23 and 24, the stepped support arms 43 and 43 are perpendicular to the axial direction of the rotary shaft 2 and are parallel to each other by using fastening means such as screws. It is fixed at each. The support arms 43 and 43 are formed in a step shape by sequentially connecting the three arm members 43 a to 43 c in the axial direction of the rotary shaft 2. In this way, the positional deviation in the axial direction of the fixed disk 22 and the non-fixed disk 24 is corrected, and it is simply connected to the stays 41s to 41s of the wings 41 and 41 that are symmetrically arranged in the same shape. It is possible.

  Further, a load cell 51 is provided as a torque detector between the fixed disk 22 and the non-fixed disk 24 so that the torque applied to the fixed disk 22 side from the non-fixed disk 24 side can be detected. This torque can be handled as the torque of the torque generator 3B alone (see FIG. 2).

  A method of attaching the load cell 51 will be described in detail with reference to FIG. This figure is an enlarged view taken along the line XX in FIG. 3 and a part thereof is broken. A stepped support arm 43 is fixed to the back side of the upper non-fixed disk 24, and a linear support arm 42 is fixed above the fixed disk 22 below. As described above, the support arm 42 is configured as a part of the torque measurement non-target portion 3 </ b> A and is rotated integrally with the rotary shaft 2. The support arm 43 is configured as a part of the torque measurement target portion 3 </ b> B, and is capable of relative rotation while maintaining the same axis as the rotation shaft 2. That is, the support arms 42 and 43 can rotate around the same rotation center 2 c, and the rotation center 2 c is the same as the axis center of the rotation shaft 2.

  In the drawing, since a part of the non-fixed disk 24 is shown in a broken state, the load cell 51 provided on the fixed disk 22 appears. The load cell 51 is not fixed as a relative rotating portion that is rotatable relative to the rotating shaft 2 and a fixed bracket 26 provided on the upper surface of the fixed disk 22 as an integrally rotating portion that rotates integrally with the rotating shaft 2. It is installed using a non-fixed side bracket 27 provided on the lower surface of the disc 24.

  Specifically, each of the fixed side bracket 26 and the non-fixed side bracket 27 has an L-shaped cross section, and one of the two orthogonal outer surfaces forming the L shape is fixed to the fixed disk 22. Or the lower surface of the non-fixed disc 24. The other surfaces are arranged so as to face each other, and these facing surfaces are connected to one end and the other end of the load cell 51. That is, the fixed side bracket 26 and the non-fixed side bracket 27 are connected via the load cell 51. Further, the load cell 51 is arranged perpendicularly to the opposing surfaces of the fixed side bracket 26 and the non-fixed side bracket 27, and it is possible to detect the force generated in the direction perpendicular to the rotating shaft 2 between them. Yes. By using the detected value from the load cell 51, it is possible to calculate the torque applied to the rotating shaft 2 from the torque generating unit 3B alone as will be described later. Further, since the load cell 51 is of a type that can detect both the tension and compression, the torque generated by the torque generator 3B can be detected in both positive and negative directions.

  Further, by being connected via the load cell 51, the non-fixed disk 24 is elastically supported in the rotation direction with respect to the rotation shaft 2. This elastic support strength can be changed according to the specifications of the load cell 51. When the sensitivity of the load cell is increased, the support force is weakened. However, when the sensitivity is decreased, the support force is decreased. Becomes stronger, and the position of the non-fixed disk 24, that is, the position of the torque generator 3B is stabilized. Therefore, the sensitivity of the load cell 51 should be determined within a range in which the position variation of the torque generator 3B is allowed without impairing the characteristics of the entire vertical axis type wind turbine. More specifically, during the rotational operation, the torque generation unit 3B, which is a torque measurement target unit, uses as a reference position a position where the rotational phase angle is shifted by 180 ° from the torque generation unit 3A, which is a torque measurement non-target unit. It is appropriate to be within the range of −3 ° to + 3 °.

  In this embodiment, since the load cell 51 is provided at a position shifted to the right side in the drawing in order to avoid interference with the support arms 42 and 43, a detection position 51a for the tension / compression load is provided. Is present at a position shifted by an angle φ in the clockwise direction from the center line (support arm center line) 43L of the support arm 43. Furthermore, the load detection direction by the load cell 51 is set to be a direction orthogonal to the support arms 42 and 43, that is, the left-right direction in the drawing. And it is possible to calculate a torque as follows using the detected value of the load by this load cell 51.

  FIG. 5 schematically shows the force generated in the torque generator 3 </ b> B and the force generated in the load cell 51.

  In the torque generator 3B, the wing 41 generates lift and drag by the wind, and the component force F of the resultant force orthogonal to the virtual support arm 43M contributes to the generation of the torque T. Become. Here, the virtual support arm 43M is a virtual rigid rod assumed at a position corresponding to the above-described support arm center line 43L, and the mass and deformation are ignored. From the load cell 51 at a position shifted by an angle φ in the clockwise direction from the virtual support arm 43M, a load P in a direction orthogonal to the virtual support arm 43M is detected and applied to the virtual support arm 43M side as a reaction force. . Here, assuming that the rotation center 2c and the load cell 51 are connected by a rigid virtual arm 51M, the load P is orthogonal to the component force S in the direction of compressing the virtual arm 51M and the virtual arm 51M. It can be divided into component force Q in the direction of The function as the virtual arm 51M is actually performed by the fixed disk 22.

When considered as described above, the reference attachment position 41d of the blade 41 is further away from the rotation center 2c by the rotation reference radius R, and the load detection position 51a of the load cell 51 is separated from the rotation center by the distance a. If it is in position, the balance equation is obtained as follows.
T = F ・ R = Q ・ a …………………………………………………… Formula (1)

Further, the following relationship exists between the load P and the component force Q.
Q = P · cosφ ……………………………………………………… Formula (2)

Here, when the distance between the intersection point formed by drawing a vertical straight line from the mounting position 51a of the load cell 51 toward the virtual support arm 43M and the rotation center 2c is b, the angle φ is between There is the following relationship.
cosφ = b / a ……………………………………………………… Formula (3)

The following relations are obtained from the formulas (1), (2), and (3).
T = Q · a = P · (b / a) · a = P · b Equation (4)

  Thus, the torque obtained by the torque generator 3B can be easily calculated by using the load detection value P by the load cell 51 and the distance b from the rotation center 2c in the direction in which the support arm 43 of the load cell 51 extends. It is possible.

  In order to easily perform the torque measurement as described above, the vertical axis wind turbine test apparatus 1 according to the present embodiment includes a control unit 7 as shown in FIG.

  The control unit 7 may be configured by causing a computer including an interface and a CPU to operate according to a predetermined program, or each function may be configured as an independent device. In any case, these work as a whole for the purpose of measuring the torque generated in the torque generator 3B alone under an arbitrarily set speed condition, in the present embodiment. Both are expressed as one control unit 7 without being distinguished.

  First, the control unit 7 includes a motor control unit 74 for controlling the rotation speed of the motor 57. The motor control unit 74 is given a rotation speed target value from an input unit (not shown), receives the speed detection value of the rotary shaft 2 obtained by a rotation data acquisition unit 73 described later, and performs feedback control based on this value. ing. However, when the motor 57 has a rotational speed detection function, it is also possible to configure such that feedback control is performed using this function.

  Further, the control unit 7 includes a brake control unit 75 that gives a brake operation command to the brake unit 54. The brake control unit 75 compares the preset upper limit rotational speed with the speed detection value of the rotating shaft 2 obtained by the rotation data acquisition unit 73, and outputs a brake signal when the speed detection value exceeds the upper limit speed. To give. By doing this, it is possible to prevent damage to the device by suppressing an increase in speed more than expected. In addition, an input signal for brake operation can be given to the brake control unit 75 from an input unit (not shown), and a brake operation command is given to the brake unit 54 in accordance with this input signal. It is also. By doing so, the operator can operate the brake at an arbitrary timing.

  In addition, the control unit 7 includes a single torque acquisition unit 71 that obtains torque transmitted from the torque generation unit 3B alone to the rotary shaft 2 based on a signal from the load cell 51. The load cell 51 rotates with the rotation of the rotating shaft 2, but a signal can be taken out without causing twisting of the signal cable via the slip ring 55 described above. Based on the load detection value obtained from this, the torque acquisition unit 71 calculates and outputs the torque T using the idea of the above formula (4). By doing so, it is possible to measure in detail the torque T when the rotating shaft 2 is rotating.

  Moreover, the control part 7 is provided with the total torque acquisition part 72 which acquires the torque which is acting with respect to the whole rotating shaft 2 based on this by receiving a detection value from the torque converter 52. FIG. The total torque acquisition unit 72 includes mechanical loss data set in advance, and can be output while correcting the torque value.

  The control unit 7 also includes a rotation data acquisition unit 73 that obtains rotation phase angle data based on the output signal from the rotation detector 53. The rotation detector 53 is composed of the slit plate 53a and the photoelectric sensor 53b as described above. By increasing the number of slits of the slit plate 53a, the rotation phase angle of the rotary shaft 2 can be determined finely. It has become. Therefore, the torque generator 3B can be evaluated more finely by comparing the rotational phase angle data with the torque T in the single torque generator 3B. Further, the rotation data acquisition unit 73 can also calculate the rotation speed from the rotation phase angle data, and can output this to the motor control unit 74 and the brake control unit 75 described above. Yes.

  An example of collecting measurement data using the vertical axis wind turbine testing apparatus 1 configured as described above will be described.

  First, prior to the description of a specific data collection method, parameters indicating characteristics of the blades 41 constituting the torque generating unit 3B will be described with reference to FIGS.

  FIG. 6 schematically shows the positional relationship between the blade 41 and the main flow direction W of the wind. In general, the azimuth angle θ is defined as indicating the positional relationship of the blade 41 with respect to the main flow direction W. This is expressed as an angle along the rotational direction, with the position where the leading edge is directly facing the mainstream direction W being 0 °. By changing the azimuth angle in the range of 0 ° to 360 ° according to the rotation, the blade 41 changes the direction with respect to the main flow direction W every moment. Therefore, even if the wind speed is the same, the generation direction and magnitude of lift and drag change as the azimuth angle θ changes.

  As parameters indicating the installation standards of the individual blades 41, there are those shown in FIG. Of course, the characteristic varies depending on the cross-sectional shape of the blade 41, but the chord length c is generally used as a typical numerical value. The chord length c indicates the length of the chord 41c connecting the leading edge 41a and the trailing edge 41b of the wing 41.

  Furthermore, when the reference position 41d serving as a reference when the blade 41 is attached to the support arms 42 and 43 (see FIG. 1) is considered in the chord 41c, the distance s from the leading edge 41a to the reference position 41d is also the blade This is important in considering the moment acting on 41. Further, the distance from the rotation center 2c to the reference position 41d is considered to be the rotation radius R of the blade 41, which is a factor for determining the speed of the blade 41 and also an important factor for determining the wind receiving area for taking in wind energy. It becomes. Further, the inclination of the chord 41c with respect to the tangential direction of the rotation reference circle 2d of the blade 41 passing through the reference position 41d is defined as the blade attachment angle β and has a great influence on the lift force and the drag force. The effect on lift and drag will greatly affect the efficiency of the vertical axis wind turbine.

  In addition to these, the length of the blade 41 in the longitudinal direction, the number of blades, and the like are also significant influencing factors. Furthermore, the support arms 42 and 43 (see FIG. 1) to which the wings 41 are attached can also be affected by wind resistance.

  As described above, the torque generated by the torque generators 3A and 3B including the blades 41 changes with many parameters intertwined. Furthermore, by affecting the wind flow by the blades 41 and the support arms 42 and 43, the direction and size of the wind also change. Further, such complexity is further increased by increasing the number of torque generating portions 3A and 3B. Therefore, an experiment is required to verify whether the actual phenomenon can be sufficiently reproduced even when the simulation is performed mainly by numerical analysis.

  As an experiment using the vertical axis type windmill test apparatus 1 in the present embodiment, it is conceivable that the experiment is performed by installing it in a wind tunnel capable of generating a wind at a predetermined speed.

  In such a case, the rotating shaft 2 is rotated by giving a command through the motor control unit 74 in FIG. 2 while giving a constant wind speed. At this time, since the speed of the motor 57 is feedback-controlled, it can be rotated at a constant speed that matches the rotational speed target value. At this time, when the speed is increased to an unexpected speed due to a circuit failure or a speed setting error, the brake control unit 75 generates a brake signal so that the brake 54 operates. Damage can be suppressed. At this time, it is more preferable that the drive electric signal from the motor control unit 74 to the motor 57 is cut off at the same time.

  In the single torque acquisition unit 71, based on the output signal from the load cell 51, it is possible to obtain the torque T transmitted to the rotary shaft 2 from the single torque generation unit 3B. The torque T obtained here can be handled as torque generated in the torque generating unit 3B alone by the air flow. Further, as the rotation shaft 2 rotates, the rotation data acquisition unit 73 can obtain rotation phase angle data of the rotation shaft 2. By obtaining these two data at the same time, it is possible to obtain a relationship between the azimuth angle θ and the torque T of the torque generating unit 3B alone, as shown in FIG. 8, for example. The torque T greatly changes so as to become the maximum near the azimuth angle of 90 °. Depending on the azimuth angle θ, negative torque may be generated. However, since the load cell 51 is compatible with both the tension and compression directions, it can be accurately determined whether it is positive or negative. It is possible to measure.

  Furthermore, since the total torque acquisition unit 72 shown in FIG. 2 can comprehensively measure the torque generated in the rotating shaft 2 including the torque generation units 3A and 3B, the torque T of the torque generation unit 3B alone and By comparing, it is possible to examine the mutual influence.

  In this way, since various data can be acquired simultaneously including the torque of the torque generating unit 3B alone, detailed test data that has not been obtained so far can be obtained by using this test apparatus. In addition, it is possible to more easily perform a condition search for optimizing the torque generators 3A and 3B. In addition, since detailed test data can be obtained by this test apparatus, matching with numerical analysis data is facilitated. Therefore, the validity of the simulation result using numerical analysis can be easily confirmed, and it becomes possible to elucidate a complicated phenomenon in which a large number of factors exist as described with reference to FIGS. . As a result, it is possible to search for optimum parameters such as the blade shape according to the wind conditions even by simulation using numerical analysis, and it becomes easy to develop a higher-performance vertical axis wind turbine.

  As described above, it can be said that the vertical axis wind turbine test apparatus 1 of the present embodiment can be used as an effective tool for realizing a more efficient vertical axis wind turbine. Moreover, it becomes possible to implement | achieve a more efficient vertical axis type windmill by the test method using this.

  As described above, the vertical axis wind turbine testing apparatus 1 according to the present embodiment includes the rotating shaft 2 that is rotatably supported and the torque generation that generates torque to be transmitted to the rotating shaft 2 by the flow of fluid. 3A and 3B, and at least one torque generating unit is configured to be rotatable relative to the rotary shaft 2 as a torque measurement target unit 3B, and between the rotary shaft 2 and the torque measurement target unit 3B. A torque detector 51 is provided.

  With this configuration, the torque generated by the torque generating unit 3B alone can be measured, and the torque generated by the vertical axis wind turbine can be investigated in more detail. Therefore, it is possible to strictly verify the result of the numerical analysis based on the actual phenomenon, and it is effective to realize a more efficient fluid rotary machine by optimizing the torque generators 3A and 3B. It can be used as a simple tool.

  Furthermore, an integrated rotating unit 26 that rotates integrally with the rotating shaft 2 and a relative rotating unit 27 that is integrated with the torque measurement target unit 3B and is rotatable relative to the rotating shaft 2 are provided. Since the integral rotation unit 26 and the relative rotation unit 27 are arranged to face each other, and the integral rotation unit 26 and the relative rotation unit 27 are connected via the torque detector 51, The configuration capable of obtaining the above effect can be realized simply and practically, and the relative positional relationship between the rotating shaft 2 and the torque measurement target portion 3B is substantially the same by connecting via the torque detector 51. Therefore, it is possible to perform torque measurement while maintaining the device conditions close to those of an actual vertical axis type wind turbine without impairing the characteristics of the entire vertical axis type wind turbine.

  Further, since the rotary shaft 2 is arranged in a direction perpendicular to the fluid flow direction W, it can be effectively configured as a test device for a vertical shaft type rotary machine among fluid type rotary machines, and generates torque. In a fluid rotary machine of the type in which the portions 3A and 3B change the positional relationship between the upstream side and the downstream side with respect to the rotating shaft 2 in the fluid flow, torque fluctuations due to such positional relationship changes Can be measured in detail. In addition, in a fluid rotary machine of a type having a plurality of torque generators 3A and 3B, the influence of other torque generators on the torque measurement target unit 3B can be investigated in detail by an experimental method. .

  In addition, since the fluid is air and the fluid rotary machine is configured as a windmill, the fluid rotary machine is effective as a tool for improving the efficiency of a windmill widely used for wind power generation and the like. It becomes possible to utilize it.

  Further, as described above, the vertical axis wind turbine test method according to the present embodiment uses the vertical axis wind turbine test apparatus 1 described above to detect the torque transmitted to the rotary shaft 2 by the torque measurement target unit 3B. The characteristic evaluation of the torque generating unit alone is performed by treating the detected torque as the torque generated in the torque generating unit 3B alone.

In this way, the detected torque thus obtained is used as a torque generated in the torque generators 3A and 3B alone, and is compared with the numerical analysis results separately performed by paying attention to the individual torque generators 3A and 3B. It is possible to search for an optimal shape and installation condition as a vertical axis wind turbine with higher efficiency.
Second Embodiment

  FIG. 9 shows a configuration of a test apparatus 201 for a horizontal axis type wind turbine as a test apparatus for a fluid-type rotating machine according to the second embodiment of the present invention. In the present test apparatus, the vertical axis windmill test apparatus 1 shown in FIG. 1 is rotated by 90 ° so that the upper end of the rotary shaft 2 faces upwind so that the rotary shaft 2 is parallel to the main flow direction W. FIG. 9 shows only a vertical cross section of the main part.

  Also in this case, the two torque generators 203A and 203B are provided, and both constitute a propeller. The torque generator 203A as a non-target portion for torque measurement is configured such that the wing 241 and the linear support arm 242 are integrally formed, and connected to the rotary shaft 202 via the fixed disk 221 so as to rotate integrally. It has become. In addition, the torque generation unit 203B as a torque measurement target unit is configured by integrally forming a blade 241 and a step-like support arm 243, and is connected to the non-fixed disk 223. Since the non-fixed disk 223 is rotatably supported while being axially regulated with respect to the rotating shaft 202 via the bearing 25, the torque generating portion 203B is not fixed to the rotating shaft 202 in the rotating direction. It is said that.

  The mutual relationship between the torque generators 203A and 203B and the relationship between the fixed disk 221 and the non-fixed disk 223 are the same as the mutual relationship between the torque generators 3A and 3B and the fixed disk 21 (22 in the first embodiment). ) And the non-fixed disk 23 (24) (see FIG. 2). Therefore, as in the case of the first embodiment, the torque generator 203B can be easily provided by arranging the load cell 51 (see FIG. 4) as a torque detector between the fixed disk 221 and the non-fixed disk 223. Thus, the torque transmitted to the rotating shaft 202 can be measured.

  Thus, even when configured as the horizontal axis wind turbine test apparatus 201, it is possible to measure the torque generated by the torque generator 203B alone. In the horizontal axis type windmill, since the rotation radius is different in the longitudinal direction of the blade 241, the relative speed with air is different. Further, the wing 241 and the support arms 242 and 243 to which the wings are attached are also deformed by the centrifugal force due to the increased rotational speed. In addition, since gravity affects the rotation of the blade 241, this also causes torque fluctuation. Furthermore, the horizontal axis type windmill is also characterized by being weaker to changes in the wind direction than the vertical axis type windmill. Even in the case where such a phenomenon peculiar to the horizontal axis type occurs, it is possible to obtain data experimentally by using this test apparatus, thereby optimizing the torque generators 203A and 203B. It becomes possible.

  As described above, in the present embodiment, the rotary shaft 202 is configured to be arranged in a direction parallel to the fluid flow direction W. It can be effectively configured as a test apparatus 201 for a mold rotating machine, and a torque generated under a phenomenon peculiar to a horizontal axis mold can be investigated in detail by an experimental method.

  In addition, it is possible to obtain substantially the same effect as in the case of the first embodiment described above.

  The specific configuration of each unit is not limited to the above-described embodiment.

  For example, in the above-described embodiment, the load cell 51 is used as the torque detector. However, the torque can be detected based on a slight relative displacement between the integral rotating portion 26 and the relative rotating portion 27. As long as other detection means are used as a base. A strain output may be obtained by interposing an elastic member having a strain gauge between the integral rotating portion 26 and the relative rotating portion 27, or may be constituted by various means such as a measuring means using a laser or a magnetic force. Is possible.

  In addition, the integral rotating unit 26 and the relative rotating unit 27 are arranged to face each other in the same rotation plane. However, as long as torque measurement is possible based on the relative displacement, they are separated from each other in the axial direction. It is also possible to change the position as appropriate according to the detection means to be used.

  Furthermore, in the above-described embodiment, the load cell 51 uses a type capable of detecting in both directions of tension and compression. However, a plurality of types that detect only compression or tension are used in combination. May be. Furthermore, it is not essential to place the load cell 51 in the direction shown in FIG. 4 as long as the positional relationship is clear even if the load detection direction is arranged in a direction that matches the rotation direction of the rotary shaft 2. Similarly, the torque can be calculated.

  In the above-described embodiment, a two-blade configuration including two torque generators 3A and 3B (203A and 203B) is used, but the configuration is the same even if the configuration has three or more blades. Is possible. For example, on the basis of the vertical axis type windmill of the first embodiment, it is possible to configure as a vertical axis type windmill test apparatus 301 corresponding to three blades as shown in FIG. In this case, three pairs of support arms 342 to 344 that respectively support the wings 41 (see FIG. 2) are provided, and a fixed disk 321 in which a pair of linear support arms 342 and 342 is fixed to the rotary shaft 2. , 322, and a pair of stepped support arms 343, 343, and non-fixed discs 323, 324, which are rotatable with respect to the rotary shaft 2 by bearings 25, 25, The support arms 344 and 344 are configured to be supported by non-fixed disks 325 and 326 which are rotatable with respect to the rotary shaft 2 by bearings 25 and 25, respectively. Then, by providing the load cells 51 between the fixed disk 322 and the non-fixed disk 324 and between the fixed disk 322 and the non-fixed disk 326, it is possible to detect torque at two locations at the same time. Become. Similarly, the number of blades can be further increased.

  Furthermore, it is not essential to provide the torque generating unit 3A as a torque measurement non-target part by providing the blades 41 via the support arms 42, 42 on the fixed discs 21 and 22 side. It is also possible to configure as a so-called single blade type having only the torque generating part 3B. In this case, it is appropriate to provide a balance weight on the opposite side of the torque generation unit 3B, which is the torque measurement target unit, so as not to cause rotational imbalance. It is also possible to configure both the torque generation units 3A and 3B as torque measurement target units.

  In the above-described embodiment, when the speed detection value of the rotating shaft 2 is equal to or greater than a predetermined value, the brake control unit 75 gives an operation command to the brake unit 54 so that the brake is automatically operated. Although configured, it is not essential to automatically operate the brake in the present invention. That is, in consideration of the properties as a test apparatus, it may be sufficient to configure the brake to be operated only manually by an operator.

  In the first embodiment, the vertical axis type wind turbine is configured as a test apparatus for a type including straight wings that generate torque mainly by lift, but the same applies to other types of test apparatuses. It is possible to configure. For example, even in other types of wind turbines such as paddle type, Darius type, Savonius type, etc., the torque generating part is attached to the rotary shaft 2 via the fixed disks 21 and 22 and the non-fixed disks 23 and 24, It can be set as the structure which provided the load cell 51 between these.

  Further, in the second embodiment, the propeller type horizontal axis wind turbine test apparatus is configured. However, similarly, it is configured as a multi-blade type, selwing type, Dutch type, etc. wind turbine test apparatus. Is also possible.

  In the above embodiment, the test device is configured to obtain the characteristics of the windmill. However, it is needless to say that the motor 57 can be configured as a general power generator only by replacing the motor 57 with a torque generator. It can be easily realized as a power generator capable of measuring the characteristics of a single generator. In such a case, the blade mounting angle β is changed based on the detected torque value of the torque generating unit 3B (203B) obtained through the load cell 51, and the control is automatically performed under appropriate conditions with higher efficiency depending on the situation. It can also be configured to do so.

  Moreover, in the case of said embodiment, although comprised as a testing apparatus of a windmill, it is also easy to comprise this as a testing apparatus of a turbine. Furthermore, it is also easy to apply the present invention to other fluid-type rotating machines such as a steam turbine and a gas turbine that are rotated by the flow of a fluid. It is possible to configure as a test apparatus capable of measuring the torque in the same manner even if the above is adopted.

  Other configurations can be variously modified without departing from the spirit of the present invention.

1 ... Vertical axis wind turbine testing device (fluid rotating machine testing device)
2 ... Rotary shaft 26 ... Fixed side bracket (integral rotating part)
27 ... Non-fixed side bracket (relative rotating part)
3A ... Torque generator (torque measurement non-target part)
3B ... Torque generator (torque measurement target)
41 ... Wings 51 ... Load cell (torque detector)
W ... Mainstream direction of wind (air)

Claims (6)

A rotating shaft rotatably supported;
A torque generator that generates torque to be transmitted to the rotating shaft by a fluid flow;
At least one torque generating unit is configured as a torque measurement target unit so as to be rotatable relative to the rotating shaft, and
A testing apparatus for a fluid-type rotating machine, wherein a torque detector is provided between the rotating shaft and the torque measurement target part. An integral rotating part that rotates integrally with the rotating shaft; and a relative rotating part that is integrated with the torque measurement target part and is relatively rotatable with respect to the rotating shaft. While facing the part,
2. The fluid rotating machine testing device according to claim 1, wherein the integral rotating part and the relative rotating part are connected via the torque detector. 3. The fluid rotary machine testing device according to claim 1, wherein the rotation shaft is disposed in a direction perpendicular to the fluid flow direction. 3. The fluid rotary machine testing apparatus according to claim 1, wherein the rotation shaft is arranged in a direction parallel to the fluid flow direction. 5. The fluid rotating machine testing apparatus according to claim 1, wherein the fluid is air, and the fluid rotating machine is configured as a windmill.   The torque transmitted to the rotating shaft by the torque measurement target unit is detected using the fluid rotating machine testing device according to any one of claims 1 to 5, and the detected torque is generated as a torque generated in the torque generating unit alone. A testing method for a fluid-type rotating machine, characterized in that the characteristics of a torque generating unit are evaluated by handling.

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