JP7168376B2 - Two-phase flow turbine rotor blade, two-phase flow turbine, and refrigeration cycle system - Google Patents

Description

The present disclosure provides a two-phase flow turbine rotor blade which is provided on a hub connected to a rotating shaft and is drivable by receiving a two-phase flow containing a liquid phase component and a gas phase component, and the two-phase flow turbine rotor blade. The present invention relates to a two-phase flow turbine and a refrigeration cycle system including the two-phase flow turbine.

A refrigeration cycle is known that comprises a compression stage, a condensation stage, an expansion stage and an evaporation stage. This type of refrigeration cycle is configured by arranging components such as compressors, condensers, expansion valves, and evaporators corresponding to each process on a circulation path through which a working fluid (refrigerant) flows. is used for When the refrigeration cycle functions as cooling, the high-temperature compressed working fluid generated in the compression process is liquefied in the condensation process, decompressed in the expansion process, and then vaporized in the evaporation process to generate cold heat.

In a typical refrigeration cycle, the expansion process involves decompression of the liquefied working fluid using a device such as an expansion valve. Arranging a two-phase turbine that can be driven by a refrigerant (two-phase flow) is disclosed to improve system efficiency by recovering the expansion energy generated in the expansion process. Further, Patent Literature 2 discloses an example of a two-phase flow turbine.

Japanese Utility Model Laid-Open No. 61-98954 U.S. Pat. No. 5,467,613

Two-phase flow turbines as disclosed in Patent Documents 1 and 2 use a two-phase flow containing a gas phase component and a liquid phase component as a working fluid. A two-phase flow turbine has at least one rotor blade (typically a plurality of rotor blades) on a hub connected to a rotating shaft, and the rotor blade receives the two-phase flow discharged from a nozzle. thereby driving a rotating shaft connected to the hub.

FIG. 11 is a schematic diagram showing how a two-phase flow 4 discharged from a nozzle 2 drives a rotor blade 8 on a hub 6 in a typical two-phase flow turbine 1. FIG. FIG. 11(a) shows how the rotor blades 8 on the hub 6 are driven by the gas phase component (gas component) 4a of the two-phase flow 4, and FIG. It shows how the rotor blades 8 on the hub 6 are driven by the liquid phase component (droplet component) 4b.

The two-phase flow turbine 1 has a plurality of moving blades 8 arranged along the circumferential direction on a hub 6 connected to a rotating shaft (not shown). Receiving the flow 4 drives the axle together with the hub 6 . In other words, the nozzle 2 is arranged at a position facing at least one of the rotor blades 8 at a predetermined timing. In FIG. 11, for the sake of simplicity of explanation, attention is paid to one of a plurality of rotor blades 8 provided on the hub 6 at substantially equal intervals along the circumferential direction. are shown driven by two-phase flow.

The gas-phase component 4a contained in the two-phase flow 4 has the property of spreading rapidly toward the surroundings when discharged from the nozzle 2, and forms an equilibrium pressure field along the circumferential direction of the hub 6. FIG. Therefore, as shown in FIG. 11(a), the gas phase component 4a forms a flow path around the hub 6 along the circumferential direction. As a result, the gas phase component 4a is received substantially perpendicularly to the rotor blades 8 provided on the hub 6 (in other words, in the tangential direction of the hub 6) regardless of the position of the rotor blades 8 at any of positions A to E. and drives the rotor blades 8 favorably.

On the other hand, the liquid phase component 4b contained in the two-phase flow 4 is composed of droplets having a larger mass than the gas phase component 4a. Therefore, as shown in FIG. 11(b), the liquid phase component 4b ejected from the nozzle 2 has strong straightness. As a result, the liquid phase component 4b discharged from the nozzle 2 can suitably transmit power to the moving blade 8 when received substantially perpendicularly to the moving blade 8, for example, at position B or C. However, at other positions such as positions A, D, and E, which are obliquely received with respect to the rotor blade 8, the radial component of the power of the liquid phase component 4b is not a little lost.

For example, when the rotor blade 8 is a three-dimensional blade, such a loss of the radial component of the power may be suppressed by devising the shroud structure and controlling the flow path of the two-phase flow. However, design changes to the three-dimensional blade and shroud structure generally increase costs. Also, such a solution cannot be applied to designs that do not have a shroud structure in the first place.

At least one embodiment of the present invention has been devised in view of the above circumstances, and is capable of achieving good power recovery efficiency in a rotor blade driven by a two-phase flow containing a liquid phase component using a simple configuration. An object of the present invention is to provide a two-phase turbine rotor blade, a two-phase turbine including the two-phase turbine rotor blade, and a refrigeration cycle system including the two-phase turbine.

(1) In order to solve the above problems, the two-phase flow turbine rotor blade according to at least one embodiment of the present invention includes:
A two-phase flow turbine rotor blade provided on a hub connected to a rotating shaft and drivable by receiving a two-phase flow containing a liquid phase component and a gas phase component,
a blade body secured to the hub and having a pressure surface that receives the two-phase flow;
at least one groove extending on the pressure surface so as to intersect a radial direction of the rotating shaft;
Prepare.

According to the above configuration (1), at least one groove is provided on the pressure surface of the rotor blade body of the two-phase flow turbine rotor blade. The groove extends so as to cross the radial direction of the rotating shaft. Since the rotor blade body is fixed on a hub that rotates together with the rotating shaft, the angle at which the pressure surface receives the two-phase flow changes from moment to moment as the rotating shaft rotates. When the two-phase flow intrudes obliquely into the pressure surface, when the two-phase flow is received by the pressure surface, it is guided by the grooves on the pressure surface and turned, so that the power of the two-phase flow is generated in the radial direction. The components can be effectively taken in and contributed to the rotation of the moving blade. In this manner, since the radial component of the power of the two-phase flow can be recovered without wasting it, the two-phase flow turbine can be efficiently driven.

(2) In some embodiments, in the configuration of (1) above,
The at least one groove includes a plurality of grooves arranged parallel to each other along the radial direction.

According to the configuration (2) above, a plurality of grooves are provided on the pressure surface. Each of the grooves is arranged parallel to each other along the radial direction on the pressure surface. As a result, the radial component of the power of the two-phase flow can be recovered over a wide range on the pressure surface.

(3) In some embodiments, in the configuration of (1) above,
The at least one groove includes a single groove.

According to the configuration (3) above, a single groove is provided on the pressure surface. In this case, the processing load for forming the grooves on the pressure surface is small, and the radial component of the power of the two-phase flow can be recovered with a simple configuration.

(4) In some embodiments, in any one configuration of (1) to (3) above,
The at least one groove has an outflow crossing angle defined by a tangential direction at a radially outer edge and a normal direction to the pressure surface of 10 degrees or less.

According to configuration (4) above, the groove provided on the pressure surface has a radially outer edge with an outflow crossing angle of 10 degrees or less. By setting the crossing angle of the outflow portion of the groove portion within this range, it is possible to more effectively obtain the above-described turning action of the two-phase flow by the groove portion, and the radial direction component of the power possessed by the two-phase flow can be more efficiently obtained. can be recovered.

(5) In some embodiments, in the configuration of (4) above,
The at least one groove portion has a larger radius of curvature on the radially outer side than on the radially inner side.

According to the configuration (5) above, the groove provided on the pressure surface is formed so that the radially outer side has a larger curvature than the radially inner side. As a result, the two-phase flow can be smoothly introduced to the inside of the groove on the radially inner side, and the radial component of the power of the two-phase flow can be effectively diverted on the radially outer side. As a result, the diversion action of the two-phase flow by the grooves described above can be obtained more effectively, and the radial direction component of the power of the two-phase flow can be recovered more efficiently.

(6) In some embodiments, in any one configuration of (1) to (5) above,
The at least one groove has a reduced surface roughness compared to other areas of the pressure surface.

According to the configuration (6) above, the groove has a smaller surface roughness on the pressure surface than other regions. In general, as shown in the Moody diagram, if the roughness is rough, the pressure loss in the boundary layer increases, resulting in loss. In this configuration, by reducing the surface roughness of the main portion through which the fluid flows, the pressure loss through which the fluid flows can be reduced.

(7) In some embodiments, in any one configuration of (1) to (6) above,
the two-phase flow is supplied to the pressure surface from one side with respect to a center line along the radial direction of the pressure surface;
The at least one groove is provided on the other side of the pressure surface with respect to the center line.

With configuration (7) above, when the two-phase flow is supplied to the pressure surface from one side of the center line, the groove is provided on the other side of the pressure surface. Since the rotor blades rotate together with the hub, when the two-phase flow is supplied from one side in this way, the radial component of the power received from the two-phase flow on the other side increases. In this configuration, by providing the groove in the region where the radial component of the power received from the two-phase flow is large, the radial component of the power can be recovered more efficiently.

(8) In some embodiments, in any one configuration of (1) to (7) above,
The rotor blade body is a parallel blade.

According to the above configuration (8), the two-phase flow turbine rotor blade having the above configuration is configured as a parallel blade. Parallel blades have a uniform vertical cross-sectional shape with respect to the longitudinal direction, and have a simpler structure than three-dimensional blades with non-uniform vertical cross-sectional shapes with respect to the longitudinal direction. In this configuration, by providing grooves on the pressure surface of the rotor blade body, which is a parallel blade, the radial power of the two-phase flow can be effectively recovered even though the blade shape is simple, and good turbine efficiency can be obtained. be done.

(9) In order to solve the above problems, the two-phase flow turbine according to at least one embodiment of the present invention includes:
A two-phase flow turbine rotor blade having any one configuration of (1) to (8) above is provided.

According to the above configuration (9), the two-phase flow turbine includes the two-phase flow turbine rotor blades according to the above-described embodiments, thereby effectively recovering the radial component of the power possessed by the two-phase flow, Good turbine efficiency can be obtained.

(10) In some embodiments, in the configuration of (9) above,
The wetness of the two-phase flow at a nozzle outlet for supplying the two-phase flow to the two-phase flow turbine rotor blade or at the outlet of the two-phase flow turbine rotor blade is 80% or more.

According to the above configuration (10), good driving efficiency is obtained by operating the two-phase flow turbine in a region where the wetness is in the range and the liquid phase component is dominant.

(11) In order to solve the above problems, the refrigeration cycle system according to at least one embodiment of the present invention includes:
a refrigeration cycle including an expansion stroke;
the two-phase flow turbine according to (9) or (10) above, which can be driven by supplying the working fluid as the two-phase flow in the expansion stroke;
a generator coupled to the two-phase flow turbine;
Prepare.

According to the above configuration (11), the two-phase flow turbine is driven by supplying the working fluid as a two-phase flow in the expansion stroke of the refrigeration cycle. Since the two-phase flow turbine includes the two-phase flow turbine rotor blades according to the above-described embodiments, it is possible to effectively recover the power of the two-phase flow, including the radial component, and obtain good turbine efficiency. . A two-phase flow turbine is coupled to the generator, and electrical energy is obtained by driving the two-phase flow turbine. In this manner, in this configuration, energy can be efficiently recovered in the expansion stroke, and a high-performance refrigeration cycle system can be realized with a simple configuration.

According to at least one embodiment of the present invention, a two-phase flow turbine rotor blade capable of achieving good power recovery efficiency in a rotor blade driven by a two-phase flow containing a liquid phase component using a simple configuration; A two-phase flow turbine including two-phase flow turbine rotor blades and a refrigeration cycle system including the two-phase flow turbine can be provided.

1 is an axial cross-sectional view of a two-phase flow turbine according to at least one embodiment of the invention; FIG. FIG. 2 is a schematic diagram showing the two-phase flow turbine rotor blade of FIG. 1 together with the nozzle from the axial direction; FIG. 3 is a perspective view showing rotor blades provided on a hub from the pressure surface side; FIG. 4 is a perspective view showing a rotor blade from direction F in FIG. 3 ; FIG. 5 is a cross-sectional view in the G region of FIG. 4; It is a schematic diagram which shows the outflow part intersection angle of a groove part. FIG. 5 is a schematic diagram of a rotor blade according to a first modified example; FIG. 11 is a schematic diagram of a rotor blade according to a second modified example; FIG. 11 is a schematic diagram of a rotor blade according to a third modified example; 1 is a configuration diagram of a refrigeration cycle system according to at least one embodiment of the present invention; FIG. FIG. 2 is a schematic diagram showing how a two-phase flow discharged from a nozzle drives rotor blades on a hub in a typical two-phase flow turbine.

Several embodiments of the present invention will now be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention, and are merely illustrative examples. do not have.

1 is an axial cross-sectional view of a two-phase flow turbine 1 according to at least one embodiment of the present invention, and FIG. 2 is a two-phase flow turbine rotor blade 8 (hereinafter referred to as "rotor blade 8" as appropriate) of FIG. 2 is a schematic diagram showing the , together with the nozzle 2, from the axial direction.
In the following description, the circumferential direction, axial direction, and radial direction are defined with reference to the rotating shaft 10 of the two-phase flow turbine 1 unless otherwise specified.

The two-phase flow turbine 1 includes a rotating shaft 10 extending along the axial direction, a hub 6 connected to the rotating shaft 10 , and at least one rotor blade 8 provided on the hub 6 . A nozzle chamber 12 in which a nozzle 2 (see FIG. 2) for supplying a working fluid that is a two-phase flow 4 is arranged is provided on the upstream side of the rotor blade 8 . A turbine diffuser 14 is provided on the downstream side of the moving blades 8 to guide the working fluid that has finished working on the moving blades 8 to the outside.

The two-phase flow turbine 1 may be supplied with a working fluid that is a two-phase flow 4 from the upstream side, or may be supplied with a working fluid that is in a liquid phase state from the upstream side, and may be supplied with a reamer as a nozzle 2, for example. The shape may be used to create a two-phase flow.

As shown in FIG. 2, a plurality of rotor blades 8 are arranged on the hub 6 along the circumferential direction. A two-phase flow 4 is supplied to these rotor blades 8 from a nozzle 2 provided in a nozzle chamber 12 . A plurality of nozzles 2 are provided along the inner wall of the nozzle chamber 12 along the circumferential direction so as to correspond to the rotor blades 8 . The number of nozzles 2 may be the same as or different from the number of rotor blades 8 . The rotor blades 8 provided on the hub 6 drive the hub 6 and the rotating shaft 10 as indicated by arrows by receiving the two-phase flow discharged from the nozzle 2 .

The discharge direction of the nozzle 2 is set so that the two-phase flow 4 is along the tangential direction of the hub 6, and the rotor blades 8 receive the two-phase flow 4, as described above with reference to FIG. The moving blade 8 moves through positions A to E in order. At this time, the gas-phase component 4a contained in the two-phase flow 4 has the property of spreading rapidly toward the surroundings when discharged from the nozzle 2, and forms an equilibrium pressure field along the circumferential direction of the hub 6. Therefore, as shown in FIG. 11(a), the gas phase component 4a forms a flow path around the hub 6 along the circumferential direction. As a result, the gas phase component 4a is received substantially perpendicularly to the rotor blades 8 provided on the hub 6 (in other words, in the tangential direction of the hub 6) regardless of the position of the rotor blades 8 at any of positions A to E. and drives the rotor blades 8 favorably.

On the other hand, the liquid phase component 4b contained in the two-phase flow 4 is composed of droplets having a larger mass than the gas phase component 4a. Therefore, as shown in FIG. 11(b), the liquid phase component 4b ejected from the nozzle 2 has strong straightness. As a result, the liquid phase component 4b discharged from the nozzle 2 can suitably transmit power to the moving blade 8 when received substantially perpendicularly to the moving blade 8, for example, at position B or C. However, at the other positions A, D and E, it is obliquely received with respect to the rotor blade 8 . In this embodiment, even in such a case, the rotor blade 8 has the following configuration, so that good power transmission can be performed.

3 is a perspective view showing the rotor blade 8 provided on the hub 6 from the pressure surface 16 side, FIG. 4 is a perspective view showing the rotor blade 8 from the direction F in FIG. 3, and FIG. FIG. 3 is a cross-sectional view in the G region; In FIG. 3, the hub 6 side is shown below the paper surface, and the tip (tip) side is shown above the paper surface.

The rotor blade 8 has a rotor blade body 18 erected on the hub 6 so that its longitudinal direction extends along the radial direction. The moving blade main body 18 is formed as a parallel blade having a constant cross-sectional shape perpendicular to the longitudinal direction.

A blade body 18 has a pressure surface 16 for receiving the two-phase flow 4 discharged from the nozzle 2 . The pressure surface 16 is formed in a concave shape and is configured to improve power recovery efficiency when receiving the two-phase flow 4 discharged from the nozzle 2 .

At least one groove 20 is provided on the pressure surface 16 . The groove portion 20 is formed in a concave shape with respect to the surface of the pressure surface 16 and extends so as to intersect the radial direction of the rotating shaft 10 . The groove portion 20 extends from one edge to the other edge along the width direction.

In the examples of FIGS. 3 to 5, a plurality of grooves 20 are provided on the pressure surface 16 along the radial direction. The plurality of grooves 20 extend substantially parallel to each other. Each groove 20 is defined by a tip edge 22 and a hub edge 24 and is recessed between the tip edge 22 and the hub edge 24 . In this manner, a plurality of grooves 20 arranged in parallel to each other along the radial direction are provided on the pressure surface 16, so that radial power recovery of the liquid phase component 4b as described later can be performed on the pressure surface 16. It can be done over a wide range.

FIGS. 3 and 5 schematically show how the liquid phase component 4b contained in the two-phase flow 4 is supplied to such a groove portion 20. As shown in FIG. When the liquid phase component 4b is supplied obliquely to the pressure surface 16 from a predetermined direction, it first enters the groove 20 from the hub side edge 24. As shown in FIG. Then, it moves along the concave bottom portion of the groove portion 20 and is turned outward from the chip-side edge portion 22 . At this time, the radial power of the liquid phase component 4 b supplied to the pressure surface 16 acts on the rotor blade body 18 through the grooves 20 and is transmitted to the hub 6 .

Here, as shown in FIG. 6, the outflow crossing angle θ at the tip-side edge 22 which is the radially outer edge of the groove 20 is determined by defined by the line direction I and In some embodiments, the outflow crossing angle θ may be 10 degrees or less. By setting the outflow crossing angle θ within such a range, the radial movement component of the liquid phase component 4b contained in the two-phase flow 4 can be effectively diverted, and the radial power can be more efficiently applied. can be recovered to

As described above, in the present embodiment, the grooves 20 are provided on the pressure surface 16 of the parallel blade, which has a simpler configuration than the three-dimensional blade. is effectively recovered and good turbine efficiency is obtained.

Incidentally, even in the three-dimensional blade, by providing the groove portion 20 on the pressure surface 16, the radial power may be recovered more effectively.

In addition, the groove portion 20 may have a smaller surface roughness than other areas of the pressure surface 16 excluding the groove portion 20 . In general, as shown in the Moody diagram, if the roughness is rough, the pressure loss in the boundary layer increases, resulting in loss. In this configuration, by reducing the surface roughness of the main portion through which the fluid flows, the pressure loss through which the fluid flows can be reduced.

The adjustment of the surface roughness may be performed, for example, by subjecting at least one of the groove portion and the pressure surface to a predetermined surface treatment. In this case, various known methods can be employed for surface processing.

FIG. 7 is a schematic diagram of a rotor blade according to the first modification (a schematic diagram corresponding to FIG. 6). In the above-described embodiment, the groove 20 provided on the pressure surface 16 has a shape with a substantially constant curvature, but the curvature of the groove 20 may not be constant as in this modified example. . Especially in the example of FIG. 7, the groove portion 20 has a larger curvature on the radially outer side (near the tip side edge 22) than on the radially inner side (near the hub side edge 24).

In other words, the outflow crossing angle θ1 at the tip-side edge 22, which is the radially outer edge of the groove 20, is defined by the tangential direction H at the tip-side edge 22 and the normal direction I to the pressure surface 16. In addition, if the inlet crossing angle θ2 at the hub side edge 24, which is the radially inner edge, is defined by the tangential direction J at the hub side edge 24 and the normal direction I to the pressure surface 16, the outflow crossing angle The angle θ1 is configured to be smaller than the inlet crossing angle θ2. As a result, the two-phase flow 4 is smoothly taken in toward the bottom side of the groove 20 at the hub-side edge 24, and the radial direction component of the liquid-phase component 4b contained in the two-phase flow 4 is at the tip-side edge 22. can be effectively diverted and radial power can be recovered more efficiently. Also in this case, it is preferable that the outflow section crossing angle θ1 is within 10 degrees from the viewpoint of improving the power recovery efficiency.

FIG. 8 is a schematic diagram of the rotor blade 8 according to the second modification (similar to FIG. 3, it is a perspective view showing the rotor blade 8 provided on the hub 6 from the pressure surface 16 side). In this modification, the nozzle 2 is arranged such that the two-phase flow 4 is supplied to the pressure surface 16 from one side (the left side of the drawing) with respect to the center line K along the radial direction of the pressure surface 16 . Thereby, the two-phase flow 4 is obliquely supplied to the pressure surface 16 from one side of the center line K of the pressure surface 16 .

The groove portion 20 is provided on the other side (right side of the drawing) of the pressure surface 16 with respect to the center line K. As shown in FIG. As the flow path of the liquid phase component 4b on the pressure surface 16 is shown in FIG. By providing the groove portion 20 on the other side of the center line K where the radial movement component of is large, the radial power of the two-phase flow can be efficiently recovered with a simple configuration.

FIG. 9 is a schematic diagram of the rotor blade 8 according to the third modification (similar to FIG. 3, it is a perspective view showing the rotor blade 8 provided on the hub 6 from the pressure surface 16 side). A plurality of grooves 20 were provided on the pressure surface 16 in the above-described embodiment, but a single groove 20 is provided on the pressure surface 16 in this modified example. In this case, the processing load for forming the grooves 20 on the pressure surface 16 is small, and the radial power of the liquid phase component 4b can be recovered with a simple configuration.

As described above, according to each of the above-described embodiments, at least one groove portion 20 is provided on the pressure surface 16 of the rotor blade body 18 of the rotor blade 8 . The groove portion 20 extends so as to intersect with the radial direction of the rotating shaft 10 . Since the rotor blade main body 18 is fixed on the hub 6 that rotates together with the rotating shaft 10 , the angle at which the pressure surface 16 receives the two-phase flow 4 changes from moment to moment as the rotating shaft 10 rotates. When the two-phase flow 4 enters obliquely into the pressure surface 16, the two-phase flow 4 is guided by the grooves 20 on the pressure surface 16 and turned around while being received by the pressure surface 16, so that the two-phase flow It is possible to effectively take in the radial component of the power possessed by 4 and contribute to the rotation of the moving blades 8 . In this way, since the radial component of the power of the two-phase flow 4 can be recovered without wasting it, the two-phase flow turbine 1 can be efficiently driven.

In the two-phase flow turbine 1 having such moving blades 8, the radial power of the two-phase flow 4 can be effectively recovered, and good turbine efficiency can be obtained. In particular, the wetness of the two-phase flow 4 at the nozzle outlet 30 (see FIG. 2) for supplying the two-phase flow 4 to the blade 8 or at the outlet 32 of the blade 8 (see FIG. 1) is In the two-phase flow turbine of 80% or more, good driving efficiency is achieved by operating the two-phase flow turbine using the two-phase flow 4 in the region where the liquid phase component 4b is dominant due to the high wetness. is obtained.

Next, a refrigeration cycle system 100 using the two-phase flow turbine 1 will be described as one application example of the two-phase flow turbine 1 having the above configuration. FIG. 10 is a configuration diagram of a refrigeration cycle system 100 according to at least one embodiment of the invention.

The refrigerating cycle system 100 is an air conditioning system using a refrigerating cycle. In the following description, the state in which the refrigerating cycle system 100 is operated in the cooling cycle will be described, but the present invention can also be applied to the state in which the refrigeration cycle system 100 is operated in the heating cycle unless otherwise specified.

The refrigeration cycle system 100 typically includes a refrigeration cycle 102 consisting of compression, condensation, expansion and evaporation steps. The refrigerating cycle 102 is configured by arranging a compressor 106, a condenser 108, a two-phase flow turbine 1, and an evaporator 112 corresponding to each process on a circulation path 104 through which refrigerant flows. Compressor 106 is multistage and includes low pressure side compressor 106 A and high pressure side compressor 106 B arranged in series along circulation path 104 . The low pressure side compressor 106A and the high pressure side compressor 106B are coaxially connected to each other and configured to be driven by the electric motor 114 .

The high-temperature, high-pressure refrigerant discharged from the compressor 106 is sent to the condenser 108 and condensed by heat exchange with the outside air. The refrigerant condensed by the condenser 108 is sent to the two-phase flow turbine 1 via the circulation path 104 . In the two-phase flow turbine 1 , refrigerant is discharged as a two-phase flow 4 from a nozzle 2 toward moving blades 8 to drive the moving blades 8 . Thereby, the rotating shaft 10 of the two-phase flow turbine 1 is driven, and the generator 116 connected to the rotating shaft 10 is driven. Since the rotor blade 8 has at least one groove portion 20 on the pressure surface 16 which receives the two-phase flow 4 as described above, it is efficiently driven by the two-phase flow 4 containing the liquid phase component 4b. As a result, the generator 116 driven by the two-phase flow turbine 1 achieves highly efficient power generation performance.

The electrical energy generated by the generator 116 may be stored in a power storage device such as a battery (not shown), or may be directly supplied to a load that consumes the electrical energy.

The refrigerant that has finished work in the two-phase flow turbine 1 is supplied to the evaporator 112 . The evaporator 112 cools the cooling water by exchanging heat between the refrigerant and the cooling water to generate cold heat from the heat of vaporization of the refrigerant. After the heat exchange in the evaporator 112, the refrigerant is returned to the compressor 106 and the above cycle is repeated.

In the refrigerating cycle 102, part of the refrigerant condensed in the condenser 108 is supplied to the expansion valve 110 via the bypass path 118 branched from the circulation path 104 and vaporized. The refrigerant vaporized by the expansion valve 110 exchanges heat with the refrigerant in the circulation path 104 in the heat exchanger 120 , thereby changing the refrigerant supplied to the two-phase flow turbine 1 into the two-phase flow 4 . The refrigerant (gas) on bypass path 118 that has passed through heat exchanger 120 is returned to compressor 106 for recirculation.

In such a refrigeration cycle system, by arranging the two-phase flow turbine 1 in the expansion process of the refrigeration cycle 102, system efficiency can be improved by recovering the expansion energy generated in the expansion process. Particularly in this embodiment, since the two-phase flow turbine 1 having the above configuration is adopted for the expansion process, good turbine efficiency can be obtained.

As described above, according to the above-described embodiments, a two-phase flow turbine rotor blade capable of achieving good power recovery efficiency in a rotor blade driven by a two-phase flow containing a liquid phase component using a simple configuration. , a two-phase turbine including the two-phase turbine rotor blade, and a refrigeration cycle system including the two-phase turbine.

At least one embodiment of the present invention provides a two-phase flow turbine rotor blade mounted on a hub connected to a rotating shaft and drivable by receiving a two-phase flow containing a liquid phase component and a gas phase component; It can be used for two-phase flow turbines with flow turbine rotor blades and refrigeration systems with such two-phase flow turbines.

1 two-phase flow turbine 2 nozzle 4 two-phase flow 6 hub 8 two-phase flow turbine rotor blade (rotor blade)
10 Rotary shaft 16 Pressure surface 18 Blade body 20 Groove 22 Tip side edge 24 Hub side edge 100 Refrigeration cycle system 102 Refrigeration cycle 104 Circulation path 106 Compressor 108 Condenser 110 Expansion valve 112 Evaporator 114 Electric motor 116 Generator 118 Bypass route 120 heat exchanger

Claims (11)

A two-phase flow turbine rotor blade provided on a hub connected to a rotating shaft and drivable by receiving a two-phase flow containing a liquid phase component and a gas phase component,
a blade body secured to the hub and having a pressure surface that receives the two-phase flow;
at least one groove extending on the pressure surface so as to intersect a radial direction of the rotating shaft;
with
A two-phase flow turbine rotor blade, wherein the two-phase flow has a wetness of 80% or more at a nozzle exit portion for supplying the two-phase flow to the two-phase flow turbine rotor blade. 2. The two-phase flow turbine rotor blade according to claim 1, wherein said at least one groove includes a plurality of grooves arranged parallel to each other along the radial direction. 2. The two-phase flow turbine rotor blade of claim 1, wherein said at least one groove comprises a single groove. 4. The at least one groove according to any one of claims 1 to 3, wherein the outflow intersection angle defined by the tangential direction at the radially outer edge and the normal direction of the pressure surface is within 10 degrees. A two-phase flow turbine rotor blade as described. 5 . The two-phase flow turbine rotor blade according to claim 4 , wherein the at least one groove portion has a greater curvature on the radially outer side than on the radially inner side. 6. The two-phase flow turbine rotor blade according to any one of claims 1 to 5, wherein said at least one groove portion has a smaller surface roughness than other areas of said pressure surface. the two-phase flow is supplied to the pressure surface from one side with respect to a center line along the radial direction of the pressure surface;
The two-phase flow turbine rotor blade according to any one of claims 1 to 6, wherein the at least one groove portion is provided on the other side of the pressure surface with respect to the center line. 8. A two-phase flow turbine rotor blade according to any one of claims 1 to 7, wherein said rotor blade body is a parallel blade. A two-phase flow turbine comprising a two-phase flow turbine rotor blade according to any one of claims 1 to 8. 10. The two-phase flow turbine according to claim 9, wherein the wetness of said two-phase flow at a nozzle outlet for supplying said two-phase flow to said two-phase flow turbine rotor blade is 80% or more. a refrigeration cycle including an expansion stroke;
11. The two-phase flow turbine according to claim 9 or 10, which can be driven by supplying the working fluid as the two-phase flow in the expansion stroke;
a generator coupled to the two-phase flow turbine;
A refrigeration cycle system.

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