Fluid machine and heat cycle system

Abstract

To regulate a flow rate with the same head and promptly regulate the flow rate for a short time without changing rotational frequency of a fluid machine and without deteriorating efficiency drastically.SOLUTION: A fluid machine 10 includes: a rotating structure 20 having an impeller 21; a casing 30 having a shroud wall 31; a first member 40 that is provided downstream of the impeller 21 and enables relative displacement to the shroud wall 31 and of which projecting amount AP to a flow passage FP is variable; and a second member 50 capable of regulating a flow of fluid FL along the shroud wall 31 toward the impeller 21 on the upstream side of the impeller 21.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a fluid machine and a thermal cycle system.

Background Art

[0002] Conventionally, a turbo compressor provided with a suction vane is known. In such a compressor, by changing the angle of the suction vane, an appropriate amount of swirling flow is given in advance to the flow of the fluid on the suction side of the impeller.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] Generally, regarding the relationship between the flow rate Q and the head H of a turbo fluid machine (QH curve), it is known that when the head is the same, the flow rate at the same rotational speed does not change. In a conventional fluid machine provided with a suction vane, it is difficult to adjust the flow rate at the same head without reducing the efficiency, and there is a problem that the time delay from the operation of the suction vane until the flow rate actually changes is large.

[0005] One aspect of the present invention is to provide a fluid machine and a thermal cycle system that can adjust the flow rate at the same head without significantly reducing the efficiency and without changing the rotational speed of the fluid machine, and can perform the flow rate adjustment quickly and in a short time.

Means for Solving the Problems

[0006] A fluid machine according to an aspect of the present invention includes a rotating structure having an impeller with a vane main plate and vanes, and a rotating shaft that rotatably supports the impeller, a casing that rotatably houses the rotating structure and has a shroud wall facing the vanes, a main plate side wall facing the vane main plate, an inlet through which fluid flows in, and an outlet through which the fluid flows out, a flow path through which at least a part of the fluid flows in a first direction from the inlet toward the outlet, a first member provided downstream of the impeller between the main plate side wall and the shroud wall, being relatively movable with respect to the shroud wall, and having a variable protrusion amount with respect to the flow path in the vicinity of the downstream end of the impeller, and a second member disposed on the shroud wall upstream of the impeller in the first direction and capable of adjusting the flow of the fluid along the shroud wall toward the impeller in the first direction.

[0007] In the fluid machine according to an aspect of the present invention, the second member has an upstream surface located on the upstream side of the second member and a downstream surface located on the downstream side of the second member, and the second member may be configured to reduce the flow rate of the fluid flowing toward the downstream side of the downstream surface rather than the flow rate of the fluid flowing toward the upstream surface among the fluid flowing along the shroud wall toward the impeller.

[0008] In the fluid machine according to an aspect of the present invention, in the radial direction of the flow path in a cross section of the flow path parallel to the direction orthogonal to the first direction, the second member is relatively movable with respect to the shroud wall, and by moving the second member with respect to the shroud wall, the second member may be configured to reduce the flow rate of the fluid in the vicinity of the shroud wall.

[0009] In the fluid machine according to an aspect of the present invention, the second member has an elastic member that forms a part of the shroud wall, and by deforming the elastic member, the second member may be configured to reduce the flow rate of the fluid in the vicinity of the shroud wall.

[0010] In a fluid machine according to one aspect of the present invention, the second member has an upstream protrusion disposed on the inner wall of the flow path on the upstream side in the first direction, and a downstream protrusion disposed on the inner wall of the flow path on the downstream side of the upstream protrusion in the first direction. In the circumferential direction of the flow path in a cross section of the flow path parallel to the direction orthogonal to the first direction, the upstream protrusion and the downstream protrusion are relatively rotatable with respect to each other. By the relative rotation of the upstream protrusion and the downstream protrusion, the second member may be configured to reduce the flow rate of the fluid in the vicinity of the shroud wall.

[0011] In a fluid machine according to one aspect of the present invention, the second member has a shaft portion extending in a direction intersecting the radial direction of the flow path and intersecting the first direction in a cross section of the flow path parallel to the direction orthogonal to the first direction. By rotating the second member around the shaft portion, the second member may be configured to reduce the flow rate of the fluid in the vicinity of the shroud wall.

[0012] In a fluid machine according to one aspect of the present invention, the second member has a shaft portion extending in the radial direction of the flow path in a cross section of the flow path parallel to the direction orthogonal to the first direction. By rotating the second member around the shaft portion, the second member may be configured to reduce the flow rate of the fluid in the vicinity of the shroud wall.

[0013] In a fluid machine according to one aspect of the present invention, the impeller has an impeller inlet located upstream of the impeller in the flow path and communicating with the flow path. By adjusting the distance between the second member and the impeller inlet in the first direction, the second member may be configured to reduce the flow rate of the fluid in the vicinity of the shroud wall.

[0014] A fluid machine according to one aspect of the present invention includes a rotating structure having an impeller with a main impeller plate and an impeller plate, and a rotating shaft that rotatably supports the impeller, a casing that rotatably houses the rotating structure and has a shroud wall facing the impeller plate, a main plate side wall facing the main impeller plate, an inlet through which a fluid flows in, and an outlet through which the fluid flows out, a flow path through which at least a part of the fluid flows in a first direction from the inlet toward the outlet, and a first member provided downstream of the impeller between the main plate side wall and the shroud wall, being relatively movable with respect to the shroud wall, having a variable protruding amount with respect to the flow path in the vicinity of the downstream end of the impeller, and having a protruding portion protruding toward the upstream side in the first direction.

[0015] In the fluid machine according to one aspect of the present invention, when viewed in the axial direction in which the rotating shaft extends, the first member may be disposed at a position radially away from the rotating shaft.

[0016] In the fluid machine according to one aspect of the present invention, when viewed in the axial direction, the first member may have an annular shape.

[0017] In the fluid machine according to one aspect of the present invention, when viewed in the axial direction, the first member may have a circular shape, an oval shape, an elliptical shape, or a polygonal shape.

[0018] In the fluid machine according to one aspect of the present invention, when viewed in the axial direction, the first member may have a non-annular shape.

[0019] In the fluid machine according to one aspect of the present invention, when viewed in the axial direction, the first member has a plurality of divided portions arranged radially from the rotating shaft, and the plurality of divided portions may be spaced apart along the circumferential direction of the first member.

[0020] In the fluid machine according to one aspect of the present invention, the first member has the plurality of divided portions and a gap portion where the plurality of divided portions are not formed in the circumferential direction. When the area ratio of the first member in the annular shape where the gap portion is not formed is set to 1.0 when viewed in the axial direction, the total area ratio of the gap portions formed along the circumferential direction when viewed in the axial direction may be 0.2 or less.

[0021] In the fluid machine according to one aspect of the present invention, the first member has a protrusion protruding toward the upstream side in the first direction and a base extending in the extending direction in which the first member extends. The protrusion has a first extending portion facing the main board side wall, and the first extending portion is provided in a part of the base and may extend from the base toward the impeller.

[0022] In the fluid machine according to one aspect of the present invention, the first member has a second extending portion facing the first extending portion, the base has a housing region housed in the shroud wall, and the second extending portion may be provided in the housing region.

[0023] In the fluid machine according to one aspect of the present invention, the first member has a protrusion protruding toward the upstream side in the first direction and a base extending in the extending direction in which the first member extends. The base has a base upstream surface facing the impeller, and the protrusion may have a recess provided on the base upstream surface.

[0024] In the fluid machine according to one aspect of the present invention, the cross-sectional shape of the recess may be a shape having at least one of a curved portion and an angular portion.

[0025] In the fluid machine according to one aspect of the present invention, the first member has a base extending in the extending direction in which the first member extends. The base may have a base upstream surface facing the impeller, a base downstream surface on the side opposite to the base upstream surface, and a through hole provided in the base so as to extend from the base upstream surface toward the base downstream surface.

[0026] In a fluid machine according to one aspect of the present invention, the first member has a tip portion located at the most distal end among the portions of the first member protruding into the flow path, and the tip portion is disposed at a minimum position where the first member is accommodated inside the shroud wall and the protruding amount of the first member is minimized, a maximum position where the protruding amount of the first member protruding from the shroud wall toward the flow path is maximized, and an intermediate position between the maximum position and the minimum position.

[0027] In a fluid machine according to one aspect of the present invention, when the tip portion is disposed at the minimum position, the fluid may flow through the flow path from the inlet toward the outlet without colliding with the first member.

[0028] In a fluid machine according to one aspect of the present invention, when the tip portion is disposed at the maximum position or the intermediate position, a first region, a second region, and a third region are formed in the flow path between the impeller and the shroud wall. In the first region, the fluid flows through the flow path from the inlet toward the outlet without colliding with the first member. In the second region, the fluid flows toward the first member and collides with the first member. In the third region, the fluid that has collided with the first member may flow in a second direction opposite to the first direction.

[0029] In a fluid machine according to one aspect of the present invention, the impeller has an impeller outlet located downstream of the impeller in the flow path, the impeller has an impeller inlet located upstream of the impeller in the flow path and communicating with the flow path, the impeller has a partition member facing the shroud wall, the partition member has an impeller opening located closer to the impeller inlet than the impeller outlet, the partition member is located at a boundary between the second region and the third region, and the fluid may flow from the third region into the second region through the impeller opening.

[0030] In a fluid machine according to one aspect of the present invention, the impeller has an impeller outlet located on the downstream side of the impeller in the flow path. Regarding the angle of the blade plate in the second region near the impeller outlet, when the angle of the blade plate is set to 0 degrees with respect to the radial direction of the impeller and the angle of the blade plate is set to a positive value with respect to the rotational direction of the impeller, the maximum value of the angle of the blade plate may be 0 degrees or a positive value.

[0031] In a fluid machine according to one aspect of the present invention, the impeller has an impeller outlet located on the downstream side of the impeller in the flow path. Regarding the angle of the blade plate in the third region near the impeller outlet, when the angle of the blade plate is set to 0 degrees with respect to the radial direction of the impeller and the angle of the blade plate is set to a positive value with respect to the rotational direction of the impeller, the minimum value of the angle of the blade plate may be 0 degrees or a negative value.

[0032] In a fluid machine according to one aspect of the present invention, the first member has a base portion extending in an extending direction in which the first member extends. The base portion has a base upstream surface facing the impeller, a base downstream surface on the side opposite to the base upstream surface, and a through hole provided in the base portion so as to extend from the base upstream surface toward the base downstream surface. A part of the fluid flowing through the flow path may flow through the through hole in the second direction opposite to the first direction, reach the base upstream surface, and merge with the fluid flowing into the second region.

[0033] In a fluid machine according to one aspect of the present invention, when the fluid flowing through the through hole in the second direction merges with the fluid flowing into the second region, a merged fluid is generated on the base upstream surface, and the merged fluid may accelerate the flow of the fluid in the third region.

[0034] A fluid machine according to one aspect of the present invention may be connected to the first member and may have a first driving unit that relatively moves the first member with respect to the shroud wall.

[0035] A fluid machine according to one aspect of the present invention may have a second drive unit that is connected to the second member and relatively moves the second member with respect to the shroud wall.

[0036] A fluid machine according to one aspect of the present invention has a first drive unit that is connected to the first member and relatively moves the first member with respect to the shroud wall, and the first drive unit and the second drive unit may move the first member and the second member so that the first member and the second member are synchronized with each other.

[0037] A fluid machine according to one aspect of the present invention has a drive unit that moves the first member and the second member, the drive unit is connected to the first member and relatively moves the first member with respect to the shroud wall, the drive unit is connected to the second member and relatively moves the second member with respect to the shroud wall, and the drive unit may move the first member and the second member so that the first member and the second member are synchronized with each other.

[0038] In a fluid machine according to one aspect of the present invention, the impeller has side plates joined to the blade plates so as to be separated from the main blade plates, and the side plates may face the shroud wall.

[0039] A thermal cycle system according to one aspect of the present invention includes a fluid machine according to the above-described aspect.

Advantages of the Invention

[0040] According to one aspect of the present invention, it is possible to adjust the flow rate at the same head without changing the rotational speed of the fluid machine and without significantly reducing the efficiency, and the flow rate adjustment can be performed quickly and in a short time.

Brief Description of the Drawings

[0041]

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Mode for Carrying Out the Invention

[0042] The fluid machine and the thermal cycle system according to the embodiment of the present invention will be described with reference to the drawings. In the description of the embodiment, the same reference numerals are given to configurations having the same or similar functions. And the overlapping description of those configurations may be omitted. The drawings are schematic or conceptual, and the relationship between the thickness and width of each part, the ratio of the sizes between parts, etc. are not necessarily the same as the actual ones.

[0043] In the description of the embodiments, ordinal numbers such as "first", "second", and "third" may be used. These ordinal numbers do not indicate the number of members described by the ordinal numbers. Ordinal numbers may be used to indicate that each of a plurality of members is a separate member.

[0044] The term "opposite" is a term indicating the positional relationship between two members. In this positional relationship, it means not only that the two members are opposite to each other, but also that there are other members intervening between the two members. The same interpretation also applies to the terms "provided", "arranged", and "connected".

[0045] In the description of the fluid machine, as terms of direction, the terms "axial direction AD", "radial direction RD", "circumferential direction CD", "first direction FD", and "second direction SD" are used. The axial direction AD is the direction in which the rotation axis 22 of the rotating structure 20 extends. The radial direction RD is the direction from the center to the outer periphery of the blade main board 24 of the rotating structure 20. The circumferential direction CD is the direction along the outer periphery of the blade main board 24 of the rotating structure 20. The first direction FD is the direction in which the fluid FL flows from the inlet 33 to the outlet 34 of the casing 30. The second direction SD is the direction opposite to the first direction FD. The terms "axial direction AD", "radial direction RD", "circumferential direction CD", "first direction FD", and "second direction SD" are terms used to describe the mutual positional relationship of a plurality of members constituting each fluid machine, or the shape and structure of each of the plurality of members, and do not define the posture of each fluid machine.

[0046] <First Embodiment> <Fluid Machine> As shown in FIG. 1, the fluid machine 10 includes a rotating structure 20, a casing 30, a flow path FP, a first member 40, a second member 50, a first drive unit D1, and a second drive unit D2. The fluid machine 10 according to the present embodiment is a horizontal-axis pump including a so-called open impeller. Note that the structure of the fluid machine 10 can also be applied to known pumps such as axial flow pumps, mixed flow pumps, and centrifugal pumps, and compressors.

[0047] <Rotating structure> The rotating structure 20 includes an impeller 21, a rotating shaft 22, and a support member 23. The impeller 21 includes an impeller main plate 24 and a plurality of blade plates 25. The impeller main plate 24 is a member that supports the blade plates 25. The impeller main plate 24 and the plurality of blade plates 25 constitute a so-called impeller. The rotating structure 20 is configured to rotate inside the casing 30 around the axial direction AD.

[0048] Furthermore, the impeller 21 has an impeller inlet 26 and an impeller outlet 27. The impeller inlet 26 is located upstream of the impeller 21 in the flow path FP. The impeller inlet 26 communicates with the flow path FP. The impeller inlet 26 is a part of the rotating structure 20 where the fluid FL flows into the impeller 21. The impeller outlet 27 is located downstream of the impeller 21 in the flow path FP. The impeller outlet 27 communicates with the flow path FP. The impeller outlet 27 is a part of the rotating structure 20 where the fluid FL flows out of the impeller 21.

[0049] <Blade plate> The plurality of blade plates 25 are provided on the impeller main plate 24 so as to extend from the impeller main plate 24 in the axial direction AD. The plurality of blade plates 25 are arranged in the circumferential direction CD of the impeller main plate 24. The shape of each of the plurality of blade plates 25 is not particularly limited. Each of the plurality of blade plates 25 may have a curved surface extending from the central region to the outer peripheral region of the impeller main plate 24. The height of each of the plurality of blade plates 25 from the impeller main plate 24 may be set to change in the radial direction RD. The shape of each of the plurality of blade plates 25 may have a curved surface that changes in the radial direction RD.

[0050] The impeller 21 is fixed to the rotating shaft 22. As the rotating shaft 22 rotates, the impeller 21 is rotatable. The support member 23 is disposed between the casing 30 and the rotating shaft 22. The support member 23 includes a bearing and a seal member. The bearing rotatably supports the rotating shaft 22. The seal member is, for example, a mechanical seal. The rotating shaft 22 is connected to a drive device (not shown). When the power generated in the drive device is transmitted to the rotating shaft 22, the rotating shaft 22 rotates, and the impeller 21 rotates as the rotating shaft 22 rotates. The drive device is, for example, a known motor.

[0051] <Casing> The casing 30 has a shroud wall 31, a main board side wall 32, an inlet 33, and an outlet 34. The shroud wall 31 rotatably houses the rotating structure 20 and faces the impeller plate 25. The main board side wall 32 faces the impeller main board 24. The fluid FL flows into the inlet 33. In other words, the inlet 33 is a suction port that sucks the fluid FL toward the casing 30. The fluid FL flows out from the outlet 34. In other words, the outlet 34 is a discharge port that discharges the fluid FL from the casing 30.

[0052] As shown in FIGS. 2A and 2B, the casing 30 has a first member housing groove 35 provided in the shroud wall 31. The first member 40 is housed in the first member housing groove 35 and is movable in the extending direction of the first member housing groove 35.

[0053] <Flow path> The flow path FP is the space between the inlet 33 and the outlet 34 in the casing 30. In this space, at least a part of the impeller main board 24, a plurality of impeller plates 25, at least a part of the first member 40, and at least a part of the second member 50 are disposed. At least a part of the fluid FL flows in the first direction FD from the inlet 33 toward the outlet 34 in the flow path FP.

[0054] <First member> The first member 40 is provided on the downstream side of the impeller 21 between the main board side wall 32 and the shroud wall 31. In other words, the first member 40 is located in the downstream region DR on the downstream side of the impeller 21. The first member 40 is movable relative to the shroud wall 31. The protruding amount AP of the first member 40 with respect to the flow path FP in the vicinity of the downstream end of the impeller 21 is variable. In other words, the protruding amount AP of the first member 40 with respect to the flow path FP in the vicinity of the impeller outlet 27 is variable.

[0055] As shown in FIGS. 2A and 2B, the first member 40 has a tip portion 41 located at the most distal end of the first member 40 protruding into the flow path FP. Regarding the protruding amount AP of the first member 40 with respect to the flow path FP, the tip portion 41 of the first member 40 can be arranged at a minimum position P0, a maximum position PX, and an intermediate position PM. Here, the minimum position P0 is a position where the first member 40 is accommodated inside the shroud wall 31 and the protruding amount AP of the first member 40 is minimized. Regarding the position of the tip portion 41 with respect to the shroud wall 31, the position of the minimum position P0 is arbitrarily set. For example, when looking in the first direction FD, a state where the position of the shroud wall 31 and the position of the tip portion 41 coincide may be defined as the protruding amount AP being arranged at the minimum position P0. Also, when looking in the first direction FD, a state where the tip portion 41 is recessed from the shroud wall 31 may be defined as the protruding amount AP being arranged at the minimum position P0. Also, when looking in the first direction FD, a state where the tip portion 41 slightly protrudes from the shroud wall 31 may be defined as the protruding amount AP being arranged at the minimum position P0. The maximum position PX is a position where the protruding amount AP of the first member 40 protruding from the shroud wall 31 toward the flow path FP is maximized.

[0056] The intermediate position PM is a position arbitrarily set between the maximum position PX and the minimum position P0. The intermediate position may be exactly at the center between the maximum position PX and the minimum position P0, or may be a position shifted from the center position. That is, the intermediate position may be closer to the maximum position PX than the minimum position P0. Also, the intermediate position may be closer to the minimum position P0 than the maximum position PX. In other words, since the intermediate position is the position of the displaceable tip 41 between the maximum position PX and the minimum position P0, the intermediate position may be referred to as a variable position.

[0057] As shown in FIG. 3A, when viewed in the axial direction AD, the first member 40 is disposed at a position radially away from the rotation axis 22. Note that FIG. 3A is a diagram for explaining the relative positions of the first member 40 and the rotation axis 22. In FIG. 3A, members other than the first member 40 and the rotation axis 22 that constitute the fluid machine 10 are omitted. In the example shown in FIG. 3A, when viewed in the axial direction AD, the first member 40 has an annular shape. In other words, the first member 40 has a circular shape. When the first member 40 has an annular shape, the shape of the first member 40 is not limited to a circular shape, and may have an oval shape, an elliptical shape, or a polygonal shape. Also, when viewed in the axial direction AD, the first member 40 may have a non-annular shape.

[0058] <Second member> The second member 50 is disposed on the shroud wall 31 upstream of the impeller 21 in the first direction FD. In other words, the second member 50 is located in the upstream region UR upstream of the impeller 21. The second member 50 can adjust the flow of the fluid FL along the shroud wall 31 toward the impeller 21 in the first direction FD.

[0059] Specifically, when the second member 50 is driven, the second member 50 can generate a stagnation in the fluid FL flowing near the shroud wall 31. In other words, it is possible to suppress the smooth flow of the fluid FL near the shroud wall 31. Also, by adjusting the amount of movement of the second member 50, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0060] In other words, the second member 50 has an upstream surface 50U located on the upstream side of the second member 50 and a downstream surface 50L located on the downstream side of the second member 50. The second member 50 can adjust the flow rate of the fluid FL flowing toward the upstream surface 50U and the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L among the fluid FL along the shroud wall 31 toward the impeller 21. In particular, the second member 50 is configured to reduce the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L rather than the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluid FL along the shroud wall 31 toward the impeller 21. "Adjustment of the flow rate" includes the meanings of "increasing the flow rate", "decreasing the flow rate", and "adjusting the flow rate ratio". Also, in the following description, mainly the reduction of the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L will be described in terms of generating the "reflux of the fluid FL" described later, but it is also possible to increase the flow rate of the fluid FL on the downstream side of the downstream surface 50L where the flow rate has decreased.

[0061] Specifically, the fluid FL flowing around the second member 50 will be described. With the driving of the fluid machine 10, the fluid FL flows from the inlet 33 toward the outlet 34. A part of the fluid FL flowing toward the second member 50 flows toward the upstream surface 50U and collides with the upstream surface 50U. The fluid FL that has collided with the upstream surface 50U forms a flow away from the shroud wall 31. The fluid FL that forms such a flow merges with the flow of other fluid FL that has not collided with the upstream surface 50U, passes over the second member 50, and flows toward the impeller inlet 26. In the flow of the fluid FL upstream of such a second member 50, the flow rate of the fluid FL flowing toward the second member 50 so as to collide with the upstream surface 50U is "the flow rate QU of the fluid FL flowing toward the upstream surface 50U". Further, the fluid FL flowing toward the upstream surface 50U is, for example, the fluid flowing through the region indicated by the reference sign UP in FIGS. 2A and 2B.

[0062] Next, a part of the fluid FL immediately after passing over the second member 50 among the fluid FL flowing from the inlet 33 toward the outlet 34 forms a flow along the downstream surface 50L and approaching the shroud wall 31. The fluid FL forming such a flow flows toward the downstream side of the downstream surface 50L. In the flow of the fluid FL downstream of such a second member 50, the flow rate of the fluid FL flowing along the downstream surface 50L and approaching the shroud wall 31 is "the flow rate QL of the fluid FL flowing toward the downstream side of the downstream surface 50L". Further, the fluid FL flowing toward the downstream side of the downstream surface 50L is, for example, the fluid flowing through the region indicated by the reference sign LP in FIGS. 2A and 2B.

[0063] By driving the second member 50, the second member 50 can reduce the "flow rate QL of the fluid FL flowing toward the downstream side of the downstream surface 50L" compared to the "flow rate QU of the fluid FL flowing toward the upstream surface 50U". In other words, the second member 50 can reduce the flow rate QL of the fluid FL flowing between the downstream surface 50L and the impeller inlet 26 (QU>QL).

[0064] <The first drive unit and the second drive unit> The first drive unit D1 is connected to the first member 40 and is configured to relatively move the first member 40 with respect to the shroud wall 31. The second drive unit D2 is connected to the second member 50 and is configured to relatively move the second member 50 with respect to the shroud wall 31. The structures of each of the first drive unit D1 and the second drive unit D2 are not particularly limited. For example, it may be a motor driven by electric power, or it may be a valve that drives each of the first member 40 and the second member 50 using the pressure of the fluid FL flowing through the fluid machine 10.

[0065] The first drive unit D1 and the second drive unit D2 may move the first member 40 and the second member 50 so that the first member 40 and the second member 50 are synchronized with each other.

[0066] <Function and effect> Next, the function and effect of the fluid machine 10 according to the first embodiment will be described. In the fluid machine 10, as the rotating structure 20 rotates, the plurality of blade plates 25 push out the fluid FL, and the fluid FL flows through the flow path FP from the inlet 33 to the outlet 34 of the casing 30. In this state, the first member 40 moves, and the protruding amount AP of the first member 40 with respect to the flow path FP is adjusted. Further, the second member 50 moves, and the degree of stagnation generated in the fluid FL is adjusted.

[0067] <Adjustment of the protruding amount by the movement of the first member> <Arrangement of the tip at the minimum position> First, as shown in FIG. 2A, the case where the tip 41 of the first member 40 is arranged at the minimum position P0 will be described. In this case, the fluid FL flows through the flow path FP from the inlet 33 to the outlet 34 without colliding with the first member 40. Specifically, when the flow rate of the fluid FL supplied to the inlet 33 of the fluid machine 10 is 100%, the flow rate of the fluid FL discharged from the outlet 34 of the fluid machine 10 is 100%.

[0068] <Movement of the tip from the minimum position to the intermediate position> The case where the tip 41 of the first member 40 moves from the minimum position P0 to the intermediate position PM by adjusting the protruding amount AP will be described. As shown in FIG. 2B, when the tip 41 of the first member 40 is arranged at the intermediate position PM, a first region R1, a second region R2, and a third region R3 are generated in the flow path FP between the impeller 21 and the shroud wall 31. In the first region R1, the fluid FL flows through the flow path FP from the inlet 33 toward the outlet 34 without colliding with the first member 40. In the second region R2, the fluid FL flows toward the first member 40 and collides with the first member 40 at a flow rate less than when the tip 41 is disposed at the maximum position PX. In the third region R3, the fluid FL that has collided with the first member 40 flows in the second direction SD opposite to the first direction FD at a flow rate less than when the tip 41 is disposed at the maximum position PX.

[0069] The operation when the tip 41 moves from the minimum position P0 to the intermediate position PM will be specifically described. The flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 when the tip 41 of the first member 40 is disposed at the minimum position P0 is taken as 100%. In this case, the flow rate of the fluid FL discharged from the outlet 34 of the fluid machine 10 is approximately 90%. The remaining 10% of the flow rate collides with the first member 40. Since the first member 40 is outside the radial direction RD from the impeller outlet 27, the velocity of the fluid FL decreases and the pressure of the fluid FL increases according to the law of conservation of angular momentum. Further, since the first member 40 exists on the downstream side in the first direction FD of the impeller outlet 27, the flow of the fluid FL is obstructed in the third region R3 as compared with the case where the first member 40 is disposed at the minimum position P0. As a result, the pressure at the impeller outlet 27 decreases. Therefore, a pressure difference occurs between the second region R2 and the third region R3. Accordingly, the fluid FL flowing in the first direction FD in the second region R2 flows in the second direction SD by colliding with the first member 40 and flows into the third region R3. In other words, a recirculation of the fluid FL occurs in the second region R2 and the third region R3. Thereby, the flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 becomes 90% of the flow rate when the tip 41 of the first member 40 is disposed at the minimum position P0. Therefore, the flow rate of the fluid machine 10 can be decreased.

[0070] The recirculation of the fluid FL in the second region R2 and the third region R3 will be described more specifically. In the following description, the fluid FL flowing in the first direction FD in the first region R1 may be referred to as fluid FL1, the fluid FL flowing in the first direction FD in the second region R2 may be referred to as fluid FL2, and the fluid FL flowing in the second direction SD in the third region R3 may be referred to as fluid FL3. The fluid FL3 flowing in the second direction SD toward the third region R3 at the impeller outlet 27 performs work on the impeller 21 in the third region R3. As the pressure of the fluid FL3 decreases, the fluid FL3 flows through the third region R3 toward the impeller inlet 26. Before reaching the impeller inlet 26, the fluid FL3 enters the second region R2 and flows through the second region R2 as fluid FL2. Here, when the fluid FL3 is converted into the fluid FL2, that is, when the fluid FL2 flows again in the first direction FD in the second region R2, the fluid FL2 is worked on by the impeller 21 and the pressure of the fluid FL2 increases. In other words, a reflux of the fluid FL occurs in the second region R2 and the third region R3. Therefore, the flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 is 90% of that when the tip 41 of the first member 40 is disposed at the minimum position P0.

[0071] Furthermore, the above-described reflux action is promoted by the second member 50. The second member 50 reduces the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L as compared with the flow rate of the fluid FL flowing toward the upstream surface 50U. For this reason, the second member 50 reduces the flow rate of the fluid FL supplied between the downstream surface 50L and the impeller 21. Thereby, the second member 50 prevents the fluid FL taken in from the inlet 33 of the fluid machine 10 from entering the third region R3. The second member 50 promotes the generation of the second region R2 and the third region R3 on the downstream side from the downstream surface 50L. Furthermore, since the first member 40 and the second member 50 are provided in the fluid machine 10, a reflux generation region is generated between the first member 40 and the second member 50, and the effects of the fluids FL2 and FL3 in the second region R2 and the third region R3 described above are promoted in the reflux generation region.

[0072] <Movement of the tip from the intermediate position to the minimum position> A case where the tip 41 of the first member 40 moves from the intermediate position PM to the minimum position P0 by adjusting the protrusion amount AP will be described. The arrangement of the tip 41 of the first member 40 returns from the arrangement shown in FIG. 2B where the tip 41 of the first member 40 is arranged at the intermediate position PM to the arrangement shown in FIG. 2A where the tip 41 of the first member 40 is arranged at the minimum position P0.

[0073] Since the fluid FL no longer collides with the first member 40, the recirculation of the fluid FL in the second region R2 and the third region R3 quickly disappears. For this reason, if the flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 when the tip 41 of the first member 40 is arranged at the minimum position P0 is taken as 100%, the flow rate of the fluid FL discharged from the outlet 34 of the fluid machine 10 becomes 100%. In other words, 10% of the flow rate that did not flow due to the decrease in the flow rate of the fluid machine 10 is quickly discharged from the outlet 34, and 10% of the flow rate is quickly sucked from the inlet 33. That is, the flow rate of the fluid FL can be quickly increased.

[0074] <Movement of the tip from the minimum position to the maximum position> A case where the tip 41 of the first member 40 moves from the minimum position P0 to the maximum position PX by adjusting the protrusion amount AP will be described. As shown in FIG. 2B, when the tip 41 of the first member 40 is arranged at the maximum position PX, a flow path FP is formed between the impeller 21 and the shroud wall 31, including a first region R1, a second region R2, and a third region R3. In the first region R1, the fluid FL flows through the flow path FP from the inlet 33 to the outlet 34 without colliding with the first member 40. In the second region R2, the fluid FL flows toward the first member 40 and collides with the first member 40. In the third region R3, the fluid FL that has collided with the first member 40 flows in the second direction SD opposite to the first direction FD.

[0075] The operation when the tip 41 moves from the minimum position P0 to the maximum position PX will be specifically described. The flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 when the tip 41 of the first member 40 is disposed at the minimum position P0 is taken as 100%. In this case, the flow rate of the fluid FL discharged from the outlet 34 of the fluid machine 10 is approximately 80%. The remaining 20% of the flow rate collides with the first member 40. Since the first member 40 is outside the radial direction RD from the impeller outlet 27, the velocity of the fluid FL decreases and the pressure of the fluid FL increases according to the law of conservation of angular momentum. Further, since the first member 40 exists on the downstream side in the first direction FD of the impeller outlet 27, in the third region R3, the flow of the fluid FL is obstructed as compared with the case where the first member 40 is disposed at the minimum position P0. Thereby, the pressure at the impeller outlet 27 becomes low. For this reason, a pressure difference occurs between the second region R2 and the third region R3. Therefore, the fluid FL flowing in the first direction FD in the second region R2 flows in the second direction SD by colliding with the first member 40 and flows into the third region R3. In other words, a recirculation of the fluid FL occurs in the second region R2 and the third region R3. Thereby, the flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 becomes 80% of the flow rate when the tip 41 of the first member 40 is disposed at the minimum position P0. Therefore, the flow rate of the fluid machine 10 can be decreased.

[0076] The recirculation of the fluid FL in the second region R2 and the third region R3 will be described more specifically. In the third region R3 of the impeller outlet 27, the fluid FL3 flowing in the second direction SD performs work on the impeller 21 in the third region R3. While the pressure of the fluid FL3 decreases, the fluid FL3 flows through the third region R3 toward the impeller inlet 26. Before reaching the impeller inlet 26, the fluid FL3 enters the second region R2 and flows through the second region R2 as the fluid FL2. Here, when the fluid FL3 is converted into the fluid FL2, that is, when the fluid FL2 flows again in the first direction FD in the second region R2, the fluid FL2 is worked on by the impeller 21 and the pressure of the fluid FL2 increases. In other words, a reflux of the fluid FL occurs in the second region R2 and the third region R3. Therefore, the flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 becomes 80% of that when the tip 41 of the first member 40 is disposed at the minimum position P0.

[0077] Furthermore, the above-described reflux action is promoted by the second member 50. The second member 50 reduces the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L as compared with the flow rate of the fluid FL flowing toward the upstream surface 50U. For this reason, the second member 50 reduces the flow rate of the fluid FL supplied between the downstream surface 50L and the impeller 21. Thereby, the second member 50 prevents the fluid FL taken in from the inlet 33 of the fluid machine 10 from entering the third region R3. The second member 50 promotes the generation of the second region R2 and the third region R3 on the downstream side from the downstream surface 50L. Furthermore, since the first member 40 and the second member 50 are provided in the fluid machine 10, a reflux generation region is generated between the first member 40 and the second member 50, and the effects of the fluids FL2 and FL3 in the second region R2 and the third region R3 described above are promoted in the reflux generation region.

[0078] <Movement of the tip from the maximum position to the minimum position> The case where the tip 41 of the first member 40 moves from the maximum position PX to the minimum position P0 by adjusting the protrusion amount AP will be described. The arrangement of the tip 41 of the first member 40 returns from the arrangement shown in FIG. 2B where the tip 41 of the first member 40 is arranged at the maximum position PX to the arrangement shown in FIG. 2A where the tip 41 of the first member 40 is arranged at the minimum position P0.

[0079] Since the fluid FL no longer collides with the first member 40, the recirculation of the fluid FL in the second region R2 and the third region R3 quickly disappears. For this reason, assuming that the flow rate of the fluid FL sucked from the inlet 33 of the fluid machine 10 when the tip 41 of the first member 40 is arranged at the minimum position P0 is 100%, the flow rate of the fluid FL discharged from the outlet 34 of the fluid machine 10 becomes 100%. In other words, 20% of the flow rate that was not flowing due to the decrease in the flow rate of the fluid machine 10 is quickly discharged from the outlet 34, and 20% of the flow rate is quickly sucked from the inlet 33. That is, the flow rate of the fluid FL can be quickly increased.

[0080] According to the above-described embodiment, by relatively moving the first member 40 with respect to the shroud wall 31, the protruding amount AP of the first member 40 with respect to the flow path FP can be adjusted. Thereby, without changing the rotational speed of the fluid machine, the flow rate at the same head can be adjusted without significantly reducing the efficiency, and the flow rate adjustment can be performed quickly and in a short time.

[0081] In the above-described embodiment, by moving the second member 50, the degree of stagnation generated in the fluid FL flowing near the shroud wall 31 can be adjusted. For this reason, compared with the case where only the first member 40 is arranged from the minimum position P0 to the intermediate position PM or the maximum position PX and the second member 50 is arranged at the position where the degree of stagnation of the fluid FL is minimized, the degree to which the flow of the fluid FL in the third region R3 is obstructed increases. For this reason, the pressure of the fluid FL3 in the third region R3 of the impeller outlet 27 becomes even lower, and the fluid FL2 flowing in the first direction FD in the second region R2 flows toward the third region R3 in the second direction SD by colliding with the first member 40, and further reflux of the fluid FL occurs in the second region R2 and the third region R3. Thereby, without changing the rotational speed of the fluid machine 10, the flow rate at the same head can be further adjusted without significantly reducing the efficiency, and the flow rate adjustment can be performed quickly and in a short time.

[0082] As described above, according to the fluid machine 10 according to this embodiment that uses the first member 40 and the second member 50, there is no need to use a high-cost pre-whirl device using a suction vane as in the prior art. In other words, according to this embodiment, with a simple structure, the above-described effects can be obtained at low cost. Furthermore, in the flow rate adjustment using a pre-whirl device, since the work done by the impeller on the fluid is reduced, generally, there is a decrease in the head that can be stably operated. Therefore, it often has a trade-off relationship with the reduction of the operable range. On the other hand, according to this embodiment, the fluids FL2 and FL3 flowing through the impeller 21 are controlled by the reflux generated in the second region R2 and the third region R3. For this reason, in principle, since there is no decrease in the head, the operable range does not decrease. Therefore, the fluid machine 10 according to this embodiment is superior to the configuration for adjusting the flow rate by the conventional pre-whirl device.

[0083] Note that the degree of flow rate reduction obtained by the fluid machine 10 is not limited to the above-described embodiments. That is, it is not limited to a flow rate reduction of 10%, 20%, etc., and the flow rate can be adjusted from several percent to several tens of percent by adjusting the protrusion amount AP of the first member 40 or the position of the second member 50.

[0084] <Modification example of the first member> Next, a modification example of the first member will be described with reference to FIG. 3B. Here, the same members described with reference to FIGS. 1 to 2B are denoted by the same reference numerals, and the description thereof is omitted or simplified.

[0085] As shown in FIG. 3B, when viewed in the axial direction AD, the first member 40A has a plurality of divided portions 42 arranged in the radial direction RD from the rotation axis 22. The plurality of divided portions 42 are arranged along the circumferential direction CD of the first member 40A. Two adjacent divided portions among the plurality of divided portions 42 are separated from each other.

[0086] The first member 40A has a plurality of divided portions 42 and a gap portion 43 in which the plurality of divided portions 42 are not formed in the circumferential direction. The gap portion 43 is formed between two adjacent divided portions. Assuming that the area ratio of the first member 40A in the annular shape where the gap portion 43 is not formed when viewed in the axial direction AD is 1.0, the total area ratio of the gap portions 43 formed along the circumferential direction when viewed in the axial direction AD is 0.2 or less. In other words, since the first member 40A shown in FIG. 3B has eight divided portions 42 and eight gap portions 43, the total area ratio of the eight divided portions 42 is 0.8 or more, and the total area ratio of the eight gap portions 43 is 0.2 or less.

[0087] In the example shown in FIG. 3B, the first member 40A has eight divided portions 42 and eight gap portions 43. The number of the divided portions 42 is not limited to eight. The number of the divided portions 42 may be seven or less, or may be nine or more. Further, regarding the length of the divided portions 42 in the circumferential direction, the lengths of at least two of the eight divided portions 42 may be the same. That is, the lengths of the eight divided portions 42 may be the same. The lengths of at least two of the eight divided portions 42 may be different from each other.

[0088] <Modification Example of the Second Member> Next, a modification example of the second member will be described with reference to FIGS. 4A to 4I. Here, the same members described with reference to FIGS. 1 to 2B are denoted by the same reference numerals, and the description thereof is omitted or simplified. In each of a plurality of modification examples, the second member is driven by a second driving unit D2. A transmission mechanism for transmitting power or a known conversion mechanism for converting the power transmission direction is provided between the second driving unit D2 and the second member.

[0089] <First Modification Example of the Second Member> As shown in FIG. 4A, the casing 30 has a second member housing groove 36 provided in the shroud wall 31. The second member 50A is housed in the second member housing groove 36 and is movable in the radial direction RD which is the extending direction of the second member housing groove 36. That is, in the radial direction RD of the flow path FP in the cross section of the flow path FP, the second member 50A is relatively movable with respect to the shroud wall 31.

[0090] Specifically, the second member 50A has two plate members 50AF and 50AS. Each of the plate members 50AF and 50AS has an end face 50AE facing the flow path FP. The plate members 50AF and 50AS are each housed in the second member housing groove 36 such that the two end faces 50AE face each other. The reference numeral 26P indicates the position of the impeller inlet 26.

[0091] Similar to the second member 50, the second member 50A has an upstream surface 50U and a downstream surface 50L. That is, each of the plate members 50AF and 50AS has an upstream surface 50U and a downstream surface 50L. The second member 50A is configured to reduce the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluids FL along the shroud wall 31 toward the impeller 21 when the second member 50A moves relative to the shroud wall 31. In other words, the second member 50A is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU > QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so that the above-described effect of the recirculation of the fluid FL can be obtained.

[0092] Specifically, when the second member 50A moves so that the end surface 50AE protrudes from the shroud wall 31, the exposed area of the upstream surface 50U in the flow path FP increases, and the exposed area of the downstream surface 50L in the flow path FP increases. The flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0093] Also, in other words, when the second member 50A moves relative to the shroud wall 31, that is, as the plate members 50AF and 50AS move relative to each other, the distance between the end surfaces 50AE of the plate members 50AF and 50AS increases or decreases. Thereby, it is possible to adjust the flow area 51 of the fluid FL flowing between the plate members 50AF and 50AS. That is, in the cross-section of the flow path FP parallel to the direction PD orthogonal to the first direction FD, that is, in the cross-section of the flow path FP parallel to the radial direction RD, the second member 50A is configured to adjust the flow area 51 of the fluid FL flowing through the flow path FP. The second member 50A configured as described above can adjust the flow of the fluid FL along the shroud wall 31 toward the impeller 21 in the first direction FD, similarly to the second member 50 described above. Therefore, by adjusting the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0094] <Second Modified Example of the Second Member> As shown in FIG. 4B, the second member 50B has two elastic members 50BF and 50BS that form part of the shroud wall 31. Each of the elastic members 50BF and 50BS has an end face 50BE facing the flow path FP. The two elastic members 50BF and 50BS can be elastically deformed so that the distance between the two end faces 50BE changes. Note that the elastic members 50BF and 50BS may be separate from the shroud wall 31. The reference numeral 26P indicates the position of the impeller inlet 26.

[0095] Similar to the second member 50, the second member 50B has an upstream surface 50U and a downstream surface 50L. That is, each of the elastic members 50BF and 50BS has an upstream surface 50U and a downstream surface 50L. In each of the elastic members 50BF and 50BS, the upstream surface 50U, the end face 50BE, and the downstream surface 50L are connected in sequence along the first direction FD. The second member 50B is configured to reduce the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluid FL along the shroud wall 31 toward the impeller 21 by deforming the elastic members 50BF and 50BS. In other words, the second member 50B is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU > QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so that the above-described effect of the recirculation of the fluid FL can be obtained.

[0096] Specifically, when the elastic members 50BF and 50BS deform so as to protrude from the shroud wall 31, the flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side rather than the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0097] In other words, the second member 50B is configured to adjust the flow area 51 by deforming each of the elastic members 50BF and 50BS. The second member 50B configured in this way can adjust the flow of the fluid FL along the shroud wall 31 toward the impeller 21 in the first direction FD, similarly to the second member 50 described above. Therefore, by adjusting the deformation amounts of the two elastic members 50BF and 50BS, that is, the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0098] <Third Modification Example of the Second Member> As shown in FIG. 4C, the second member 50C has an upstream protrusion 50CU and a downstream protrusion 50CL. The upstream protrusion 50CU is disposed on the inner wall WL of the flow path FP on the upstream side US in the first direction FD. The downstream protrusion 50CL is disposed on the inner wall WL of the flow path FP on the downstream side DS of the upstream protrusion 50CU in the first direction FD. In the circumferential direction CD of the flow path FP in the cross section of the flow path FP, the upstream protrusion 50CU and the downstream protrusion 50CL are relatively rotatable with respect to each other. The reference numeral 26P indicates the position of the impeller inlet 26.

[0099] Here, a specific description will be given with reference to FIGS. 4D and 4E. As shown in FIG. 4D, the upstream protrusion 50CU is rotatable in the clockwise direction CW or the counterclockwise direction CCW in a state of being disposed on the inner wall WL of the flow path FP as viewed in the first direction FD. On the other hand, as shown in FIG. 4E, the downstream protrusion 50CL is fixed to the inner wall WL of the flow path FP. Thereby, the upstream protrusion 50CU and the downstream protrusion 50CL are relatively rotatable with respect to each other. Note that the downstream protrusion 50CL may be rotatable in the clockwise direction CW or the counterclockwise direction CCW. In this case, the upstream protrusion 50CU is fixed to the inner wall WL of the flow path FP. Also, each of the upstream protrusion 50CU and the downstream protrusion 50CL may be rotatable. As shown in FIGS. 4D and 4E, a gap portion 50S is formed between two upstream protrusions 50CU in the circumferential direction CD. When viewed in the first direction FD, the downstream protrusion 50CL is arranged so as to overlap the gap portion 50S or the upstream protrusion 50CU. By the relative rotation of the upstream protrusion 50CU and the downstream protrusion 50CL, the area of the gap portion 50S covered by the downstream protrusion 50CL is adjusted.

[0100] Similar to the second member 50, the second member 50C has an upstream surface 50U and a downstream surface 50L. The upstream surface 50U corresponds to the surface of the upstream protrusion 50CU against which the fluid FL flowing in the first direction FD collides and the surface of the downstream protrusion 50CL that is located in the gap portion 50S and against which the fluid FL flowing in the first direction FD collides. The downstream surface 50L corresponds to the surface on the downstream side of the downstream protrusion 50CL.

[0101] The second member 50C is configured such that, when the upstream protrusion 50CU and the downstream protrusion 50CL rotate relative to each other, the flow rate of the fluid FL flowing toward the downstream surface 50L is decreased compared to the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluid FL along the shroud wall 31 toward the impeller 21. In other words, the second member 50C is configured to decrease the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU>QL). That is, it is configured to decrease the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so as to obtain the above-described effect of the recirculation of the fluid FL.

[0102] Specifically, when the upstream protrusion 50CU and the downstream protrusion 50CL rotate relative to each other, the flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0103] In other words, in response to the relative rotation of the upstream protrusion 50CU and the downstream protrusion 50CL, the flow area 51 is adjusted by adjusting the clearance area of the clearance portion 50S formed by the overlap of the upstream protrusion 50CU and the downstream protrusion 50CL as viewed in the first direction FD. The second member 50C configured in this way can adjust the flow of the fluid FL along the shroud wall 31 toward the impeller 21 in the first direction FD, similarly to the second member 50 described above. Therefore, by adjusting the relative rotation amount of the upstream protrusion 50CU with respect to the downstream protrusion 50CL, that is, the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0104] <Fourth Modification Example of the Second Member> As shown in FIG. 4F, the second member 50D has a shaft portion 50DA extending in the direction XD. Here, the direction XD is a direction that intersects the radial direction RD of the flow path FP in the cross section of the flow path FP and also intersects the first direction FD. The second member 50D, which is a plate member, is rotatably supported around the shaft portion 50DA by the shaft portion 50DA. The second member 50D is configured to adjust the flow area 51 by rotating around the shaft portion 50DA. The reference numeral 26P indicates the position of the impeller inlet 26.

[0105] Similar to the second member 50, the second member 50D has an upstream surface 50U and a downstream surface 50L. When the second member 50D rotates around the shaft portion 50DA, among the fluid FL along the shroud wall 31 toward the impeller 21, the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L is configured to be reduced compared to the flow rate of the fluid FL flowing toward the upstream surface 50U. In other words, the second member 50D is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU > QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so that the effect of the recirculation of the fluid FL described above can be obtained.

[0106] Specifically, when the second member 50D rotates around the shaft portion 50DA, the flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0107] The second member 50D configured in this way can adjust the flow of the fluid FL along the shroud wall 31 toward the impeller 21 in the first direction FD, similar to the second member 50 described above. Therefore, by adjusting the rotation amount of the second member 50D around the shaft portion 50DA, that is, the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0108] <The Fifth Modification Example of the Second Member> In Fig. 4F described above, two shaft portions 50DA are shown, but the number of the shaft portions 50DA may be three or more. As shown in Fig. 4G, the second member 50E has a structure in which six shaft portions 50DA are arranged along the inner wall WL of the flow path FP. Plate members 50EF are provided on each of the six shaft portions 50DA. The plate member 50EF is rotatably supported around the shaft portion 50DA by the shaft portion 50DA. The plate member 50EF has an upstream surface 50U and a downstream surface 50L. When the plate member 50EF rotates around the shaft portion 50DA, the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L is reduced compared to the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluids FL along the shroud wall 31 toward the impeller 21. In other words, the plate member 50EF is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU>QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so that the above-described effect of the recirculation of the fluid FL can be obtained.

[0109] Specifically, when the plate member 50EF rotates around the shaft portion 50DA, the flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0110] Also, in other words, the plate member 50EF is configured to adjust the flow area 51 by rotating around each of the six shaft portions 50DA. By adjusting the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0111] <Sixth Modified Example of the Second Member> As shown in FIG. 4H, the second member 50F has a shaft portion 50FA extending in the radial direction RD of the flow path FP in the cross section of the flow path FP. The second member 50F, which is a plate member, is rotatably supported around the shaft portion 50FA by the shaft portion 50FA. The shaft portion 50FA is provided at the downstream end of the second member 50F in the first direction FD. The reference numeral 26P indicates the position of the impeller inlet 26. Even if the second member 50F rotates around the shaft portion 50FA, the second member 50F is not arranged downstream of the position indicated by the reference numeral 26P.

[0112] Similar to the second member 50, the second member 50F has an upstream surface 50U and a downstream surface 50L. By rotating the second member 50F around the shaft portion 50FA, the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L is reduced compared to the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluid FL along the shroud wall 31 toward the impeller 21. In other words, the second member 50F is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU > QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so that the above-described effect of the recirculation of the fluid FL can be obtained.

[0113] Specifically, by rotating the second member 50F around the shaft portion 50FA, the flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side of the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0114] The second member 50F configured as described above is configured to adjust the flow area 51 by rotating around the shaft portion 50FA. Therefore, by adjusting the rotation amount of the second member 50F around the shaft portion 50FA, that is, by adjusting the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0115] <The seventh modification of the second member> In FIG. 4H described above, two shaft portions 50FA are shown, but the number of the shaft portions 50FA may be three or more. As shown in FIG. 4I, the second member 50G has a structure in which six plate members 50FF are arranged along the inner wall WL of the flow path FP. Each of the six plate members 50FF is rotatably supported around the shaft portion 50FA by the shaft portion 50FA. The plate member 50FF has an upstream surface 50U and a downstream surface 50L. By rotating the plate member 50FF around the shaft portion 50FA, the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L is reduced compared to the flow rate of the fluid FL flowing toward the upstream surface 50U among the fluids FL along the shroud wall 31 toward the impeller 21. In other words, the plate member 50FF is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU>QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so that the above-described effect of the recirculation of the fluid FL can be obtained.

[0116] Specifically, by rotating the plate member 50FF around the shaft portion 50FA, the flow rate of the fluid FL colliding with the upstream surface 50U increases. Thereby, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0117] Also, in other words, the plate member 50FF is configured to adjust the flow area 51 by rotating around each of the six shaft portions 50FA. By adjusting the flow area 51 of the fluid FL, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0118] <The eighth modification of the second member> As shown in FIG. 4J, the second member 50H is capable of adjusting the distance DT between the second member 50H and the impeller inlet 26 in the first direction FD. In FIG. 4J, reference numeral 26P indicates the position of the impeller inlet 26. Reference numeral P1 indicates the position of the second member 50H when the second member 50H is closest to the impeller inlet 26. At the position P1, the distance between the second member 50H and the impeller inlet 26 is DT1. Reference numeral P2 indicates the position of the second member 50H when the second member 50H is farthest from the impeller inlet 26. At the position P2, the distance between the second member 50H and the impeller inlet 26 is DT2. The distance DT2 is greater than the distance DT1.

[0119] Similar to the second member 50, the second member 50H has an upstream surface 50U and a downstream surface 50L. The second member 50H can be disposed between the position P1 and the position P2, and when the second member 50H is disposed at the position P1, the second member 50H can be moved closer to the impeller inlet 26. Thereby, of the fluid FL along the shroud wall 31 toward the impeller 21, the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L is configured to be reduced compared to the flow rate of the fluid FL flowing toward the upstream surface 50U. In other words, the second member 50H is configured to reduce the flow rate QL of the fluid FL flowing through the region LP compared to the flow rate QU of the fluid FL flowing through the region UP (QU>QL). That is, it is configured to reduce the flow rate QL of the fluid FL in the region LP between the downstream surface 50L and the impeller inlet 26. The distance between the downstream surface 50L and the position 26P, that is, the width of the region LP in the first direction FD, is appropriately set so as to obtain the effect of the recirculation of the fluid FL described above.

[0120] Specifically, by moving the second member 50H closer to the impeller inlet 26, it is possible to reduce the flow rate of the fluid FL flowing toward the downstream side from the downstream surface 50L compared to the flow rate of the fluid FL flowing toward the upstream surface 50U.

[0121] In other words, the flow of the fluid FL changes according to the arrangement of the second member 50H. By moving the second member 50H between the position P1 and the position P2, it is possible to adjust the degree of stagnation generated in the fluid FL.

[0122] <Modified Example of the Driving Unit> In the example shown in FIG. 1, the fluid machine 10 has a first driving unit D1 and a second driving unit D2 as two driving units. The fluid machine 10 may move the first member 40 and the second member 50 by one driving unit. That is, one driving unit is connected to the first member 40 and the second member 50, and is configured to relatively move the first member 40 with respect to the shroud wall 31 and relatively move the second member 50 with respect to the shroud wall 31. In this configuration, one driving unit may move the first member 40 and the second member 50 so that the first member 40 and the second member 50 are synchronized with each other.

[0123] <Second Embodiment> <Fluid Machine> In the above-described embodiment, the case where the fluid machine 10 includes the first member 40 capable of adjusting the protruding amount AP with respect to the flow path FP and the second member 50 capable of adjusting the flow of the fluid FL along the shroud wall 31 has been described. In the second embodiment described below, the case where the fluid machine drives only the first member without using the second member 50 will be described. Here, the same members described with reference to FIGS. 1 to 2B are denoted by the same reference numerals, and the description thereof is omitted or simplified. In addition, the illustration of the driving unit that relatively moves the first member with respect to the shroud wall 31 is omitted.

[0124] Similar to the first embodiment, the fluid machine according to the second embodiment has a rotating structure 20, a casing 30, a flow path FP, and a first driving unit D1. Furthermore, the fluid machine according to the second embodiment has a first member 60A instead of the first member 40 according to the first embodiment.

[0125] <First Member> The first member 60A has substantially the same configuration as the first member 40. On the other hand, the first member 60A is different from the first member 40 in that the first member has a protrusion. As shown in FIG. 5A, the first member 60A has a protrusion 61 and a base 62. The base 62 extends in the extending direction in which the first member 60A extends. In the present embodiment, the extending direction in which the first member 60A extends corresponds to the axial direction AD. Note that the extending direction of the first member 60A may be a direction inclined with respect to the axial direction AD.

[0126] The protrusion 61 is provided on the base 62 so as to protrude toward the upstream side in the first direction FD. The protrusion 61 has a first extending portion 63 that faces the main board side wall 32. The first extending portion 63 is provided on a part of the base 62 and extends from the base 62 toward the impeller 21. The first extending portion 63 extends in a direction parallel to the first direction FD. The first extending portion 63 has a tip portion 60X that is located at the most distal end of the first member 60A. The tip portion 60X corresponds to the tip portion 41 described above.

[0127] The first member 60A has a second extending portion 64 that faces the first extending portion 63. The base 62 has a housing region 65 that is housed in the shroud wall 31. The second extending portion 64 is provided in the housing region 65 of the base 62. The first member housing groove 35 provided in the shroud wall 31 has a width corresponding to the length of the second extending portion 64 in the first direction FD. Thereby, as the protrusion amount AP is adjusted, the first member housing groove 35 can house the second extending portion 64.

[0128] <Operational effects> Next, the operational effects of the fluid machine according to the second embodiment will be described. In the fluid machine according to the second embodiment, as the rotating structure 20 rotates, the plurality of blade plates 25 push out the fluid FL, and the fluid FL flows through the flow path FP from the inlet 33 to the outlet 34 of the casing 30. In this state, the first member 60A moves, and as described with reference to FIGS. 2A and 2B, the protrusion amount AP of the first member 60A with respect to the flow path FP is adjusted.

[0129] As shown in FIGS. 2A and 2B, by adjusting the protrusion amount AP, the tip 60X of the first member 60A can move from the minimum position P0 to the intermediate position PM, and the tip 60X of the first member 60A can move from the minimum position P0 to the maximum position PX. In this case, the fluid FL flowing in the first direction FD in the second region R2 collides with the first member 60A. The fluid FL that has collided with the first member 60A flows in the second direction SD in the third region R3. A recirculation of the fluid FL occurs in the second region R2 and the third region R3. Thereby, the flow rate of the fluid machine can be decreased. In particular, since the first member 60A has a base 62, a first extension 63, and a second extension 64, when the fluid FL flows into the region surrounded by the base 62, the first extension 63, and the second extension 64, the generation of the recirculation of the fluid FL can be promoted.

[0130] Also, by adjusting the protrusion amount AP, the tip 60X of the first member 60A can move from the intermediate position PM to the minimum position P0, and the tip 60X of the first member 60A can move from the maximum position PX to the minimum position P0. In this case, the compressed state of the fluid FL by the first member 60A is rapidly released, the recirculation of the fluid FL in the second region R2 and the third region R3 quickly disappears, the flow rate of the recirculated fluid FL is rapidly discharged from the outlet 34, and the fluid FL is newly and quickly sucked in from the inlet 33. That is, the flow rate of the fluid FL can be rapidly increased.

[0131] <Modification Example of the First Member> Next, with reference to FIGS. 5B to 5J, a modification example of the first member will be described. Here, the same members described with reference to FIGS. 1 to 2B and 5A are denoted by the same reference numerals, and their descriptions are omitted or simplified.

[0132] <First Modification Example of the First Member> The first member 60B shown in FIG. 5B is different from the first member 60A in that it does not include the second extending portion 64. That is, the first member 60B has the first extending portion 63 and the base portion 62. In the example shown in FIG. 5B, the casing 30 has a housing portion 37 provided on the shroud wall 31. The housing portion 37 has a shape corresponding to the first extending portion 63. When the tip portion 60X is disposed at the minimum position P0, the housing portion 37 is configured to house the first extending portion 63. In such a configuration, the protruding amount AP of the first member 60B with respect to the flow path FP is adjusted. In the first member 60B, the same or similar effects as those of the first member 60A can be obtained.

[0133] <First Modified Example of the First Member> The first member 60C shown in FIG. 5C is different from the first member 60B in that it extends in a direction inclined in the first direction FD. The first extending portion 63 of the protrusion 61 protrudes toward the upstream side in the first direction FD. Also in such a configuration, the protruding amount AP of the first member 60C with respect to the flow path FP is adjusted. In the first member 60C, the same or similar effects as those of the first member 60A can be obtained.

[0134] <Second Modified Example of the First Member> The first member 60D shown in FIG. 5D is different from the first member 60A in terms of the structure of the base portion 62. The base portion 62 has a first base portion 62F and a second base portion 62S. The first base portion 62F is located in the first member housing groove 35 even when the tip portion 60X is disposed at each of the minimum position P0, the intermediate position PM, and the maximum position PX. The second base portion 62S is a portion provided between the first base portion 62F and the first extending portion 63. The second base portion 62S has an inclined surface facing the upstream side in the first direction FD. The first extending portion 63 is connected to the inclined surface of the second base portion 62S. Also in such a configuration, the protruding amount AP of the first member 60D with respect to the flow path FP is adjusted. In the first member 60D, the same or similar effects as those of the first member 60A can be obtained.

[0135] <Fourth Modification Example of the First Member> The first member 60E shown in FIG. 5E is different from the first member 60A in terms of the structure of the protrusion 61 and the base 62. Similar to the first member 60A, the first member 60E has a base 62. The base 62 has a base upstream surface 62U facing the impeller 21. The protrusion 61 has a recess 62R provided on the base upstream surface 62U. The recess 62R has a bottom 62B and two inclined surfaces 62K sandwiching the bottom 62B. The bottom 62B is the part that is farthest from the base upstream surface 62U in the first direction FD among the parts forming the recess 62R. Regarding the cross-sectional shape, the bottom 62B and the two inclined surfaces 62K form a corner. The inclined surface 62K corresponds to the protrusion 61. That is, the protrusion 61 is formed around the bottom 62B. In other words, the protrusion 61 forms a part of the recess 62R.

[0136] Even in the first member 60E having such a recess 62R, the protrusion amount AP is adjusted, and the same operation as that of the first member 60A can be obtained. Specifically, as shown in FIGS. 2A and 2B, by adjusting the protrusion amount AP, the tip 60X of the first member 60E can move from the minimum position P0 to the intermediate position PM, and the tip 60X of the first member 60E can move from the minimum position P0 to the maximum position PX. In this case, the fluid FL flowing in the first direction FD in the second region R2 collides with the first member 60E and then flows in the second direction SD, and a recirculation of the fluid FL occurs in the second region R2 and the third region R3. Thereby, the flow rate of the fluid machine can be decreased. In particular, since the first member 60E has a recess 62R provided in the base 62, when the fluid FL flows into the recess 62R, the generation of the recirculation of the fluid FL can be promoted.

[0137] Also, by adjusting the protrusion amount AP, the tip 60X of the first member 60E can move from the intermediate position PM to the minimum position P0, and the tip 60X of the first member 60E can move from the maximum position PX to the minimum position P0. In this case, the compressed state of the fluid FL by the first member 60E is rapidly eliminated, and the reflux of the fluid FL in the second region R2 and the third region R3 quickly disappears. That is, the flow rate of the fluid FL can be rapidly increased.

[0138] <Fifth Modification Example of the First Member> The first member 60F shown in FIG. 5F is different from the first member 60E in terms of the cross-sectional shape of the recessed portion 62R. Specifically, the recessed portion 62R has a bottom portion 62B and a curved surface 62C located around the bottom portion 62B. Regarding the cross-sectional shape, the bottom portion 62B and the curved surface 62C form a curved portion. The curved surface 62C corresponds to the protruding portion 61. That is, the protruding portion 61 is formed around the bottom portion 62B. In other words, the protruding portion 61 forms a part of the recessed portion 62R. Even in such a configuration, the protruding amount AP of the first member 60C with respect to the flow path FP is adjusted. Also in the first member 60F, the same or similar effects as those of the first member 60E can be obtained.

[0139] <Sixth Modification Example of the First Member> Each of the first member 60G shown in FIG. 5G and the first member 60H shown in FIG. 5H is different from the first member 60F in terms of the size of the recessed portion 62R. The depth DP of the recessed portion 62R of the first member 60G is larger than the depth of the recessed portion 62R of the first member 60F in the first direction FD. The width WD of the recessed portion 62R of the first member 60H is wider than the width of the recessed portion 62R of the first member 60F in the radial direction RD. As shown in each of the first member 60G and the first member 60H, the depth DP and the width WD of the recessed portion 62R can be freely changed. Even in such a configuration, the same or similar effects as those of the first member 60E can be obtained.

[0140] <Seventh Modification Example of the First Member> The first member 60I shown in FIG. 5I is different from the first member 60F in that a through hole is provided in the base portion 62. In the first member 60I shown in FIG. 5I, the protrusion 61 and the recess 62R are omitted. The seventh modification described below can be applied to the first member having the protrusion 61 or the recess 62R.

[0141] In the first member 60I, the base portion 62 has a base upstream surface 62U facing the impeller 21 and a base downstream surface 62D on the side opposite to the base upstream surface 62U. Further, the base portion 62 has a through hole 62P provided in the base portion 62 so as to extend from the base upstream surface 62U toward the base downstream surface 62D. In other words, the through hole 62P has an opening that opens to the base upstream surface 62U and an opening that opens to the base downstream surface 62D. Note that, in the first member 60I shown in FIG. 5I, only one through hole 62P is shown, but a plurality of through holes 62P are provided in the entire first member 60I.

[0142] <Function and effect> Next, the function and effect of the fluid machine including the first member 60I will be described. In the fluid machine, when the rotating structure 20 rotates, the plurality of blade plates 25 push out the fluid FL, and the fluid FL flows through the flow path FP from the inlet 33 to the outlet 34 of the casing 30. In this state, the first member 60I having the through hole 62P moves, and as described with reference to FIGS. 2A and 2B, the protruding amount AP of the first member 60I with respect to the flow path FP is adjusted.

[0143] As shown in FIGS. 2A and 2B, by adjusting the protruding amount AP, the tip 60X of the first member 60I can move from the minimum position P0 to the intermediate position PM, and the tip 60X of the first member 60I can move from the minimum position P0 to the maximum position PX. In this case, the fluid FL flowing in the first direction FD in the second region R2 collides with the first member 60I and then flows in the second direction SD, causing a reflux of the fluid FL in the second region R2 and the third region R3. Thereby, the flow rate of the fluid machine can be reduced.

[0144] Here, the base downstream surface 62D is located outside the base upstream surface 62U in the radial direction RD. For this reason, according to the law of conservation of angular momentum, the velocity of the fluid FL flowing in the first direction FD without colliding with the first member 60I decreases toward the outside in the radial direction RD. Also, the pressure of the fluid FL flowing in the first direction FD without colliding with the first member 60I increases toward the outside in the radial direction RD. The base downstream surface 62D is located outside the base upstream surface 62U in the radial direction RD. For this reason, the pressure at the base downstream surface 62D is higher than the pressure at the base upstream surface 62U.

[0145] Since the first member 60I has the through hole 62P, a part of the fluid FL flowing through the flow path FP flows through the through hole 62P in the second direction SD. The fluid FL that has flowed through the through hole 62P reaches the base upstream surface 62U and merges with the fluid FL flowing into the second region R2. That is, the fluid FL flowing through the through hole 62P in the second direction SD and the fluid FL flowing into the second region R2 in the first direction FD merge. As a result, a merged fluid is generated at the base upstream surface 62U. The merged fluid accelerates the flow of the fluid FL in the third region R3. For this reason, by using the first member 60I having the through hole 62P, a merged fluid can be generated, and the generation of the recirculation of the fluid FL in the second region R2 and the third region R3 can be promoted.

[0146] <Eighth Modification of the First Member> The first member 60J shown in FIG. 5J is different from the first member 60I in that the through hole 62P provided in the base 62 is inclined with respect to the radial direction RD. As shown in FIG. 5J, a plurality of through holes 62P are provided in the base 62 in the circumferential direction CD. The plurality of through holes 62P are provided, for example, at equal intervals in the circumferential direction CD. Each of the plurality of through holes 62P extends so as to be inclined with respect to the radial direction RD. Even in such a configuration, the same or similar effects as those of the first member 60I can be obtained.

[0147] <Modification of the Second Embodiment> In the above-described second embodiment and the modified examples of the first member, the case where the first members 60A to 60J are applied to the fluid machine according to the second embodiment has been described. The first members 60A to 60J can also be applied to the fluid machine 10 according to the first embodiment. In this case, one of the first members 60A to 60J can cooperate with the second member 50. Also, one of the first members 60A to 60J can cooperate with one of the second members 50A to 50G described in the modified example of the first embodiment.

[0148] <Third Embodiment> <Impeller Vane> Next, the impeller vane 25 according to the third embodiment will be described. In the following description, one impeller vane 25 out of a plurality of impeller vanes 25 will be described. Here, the same reference numerals are given to the same members described with reference to FIGS. 1 to 2B, and the description thereof is omitted or simplified. In FIGS. 6A and 6B, among the components constituting the fluid machine, the components other than the impeller and the impeller vane are omitted.

[0149] FIG. 6A shows a general impeller vane 125, a general impeller main vane 124, and a general impeller outlet 127. Further, FIG. 6A shows a velocity triangle which is the velocity vector at the tip portion of the impeller vane 125 located at the impeller outlet 127. The symbol W2 means the relative velocity of the fluid with respect to the impeller (relative velocity). The symbol U2 means the peripheral velocity of the impeller main vane 124. The symbol C2 is the vector sum obtained by adding the relative velocity W2 and the peripheral velocity U2. The vector sum is the absolute velocity of the outflowing fluid FL. The description with reference to the velocity triangle will be described later.

[0150] As shown in FIG. 6A, the impeller vane 125 extends from the center of the impeller main vane 124 toward the impeller outlet 127. Here, with respect to the axis AX parallel to the radial direction RD, the angle of the impeller vane 125 at the impeller outlet 127 is defined by the symbol B. In other words, the impeller vane 125 at the impeller outlet 127 is inclined at an angle B with respect to the axis AX parallel to the radial direction RD. Regarding the sign of the value of angle B, when taking the axis AX as a reference, the angle B in the rotation direction +R of the impeller 21 is defined as a positive value (+B), and in contrast, the angle B in the reverse direction -R opposite to the rotation direction +R is defined as a negative value (-B). When the angle of the blade plate 125 is defined in this way, in the impellers of general compressors and pumps, the angle of the blade plate 125 is a negative value or 0. In particular, the angle of the blade plate 125 at the impeller inlet 26 is a negative value. The reason is as follows. The flow of the fluid flowing into the impeller is usually parallel to the axial direction AD and has no circumferential direction CD component. For this reason, with respect to the blade plate 125 that is rotating (clockwise in FIG. 6A, rotation direction +R) and has a circumferential direction CD speed, the fluid having a relative speed in the direction opposite to the circumferential direction CD flows in. It is necessary to incline the inlet of the blade plate 125 in the circumferential direction CD so that such fluid flows into the blade plate 125 without collision.

[0151] Next, referring to FIG. 6B, the present embodiment will be described. As shown in FIG. 6B, in the flow path FP between the impeller 21 and the shroud wall 31, according to the protruding amount AP of the first member, the above-described first region R1, second region R2, and third region R3 are generated. For this reason, also in the blade plate 25, the first region R1, second region R2, and third region R3 are generated. In other words, according to the height Z of the blade plate 25 in the axial direction AD, the first region R1, second region R2, and third region R3 are generated. In FIG. 6B, the symbol Z0 means the case where the height of the blade plate 25 is zero, and indicates the position of the surface of the main blade plate 24. As the height of the blade plate 25 increases from the position Z0, the first region R1, second region R2, and third region R3 are sequentially generated in the blade plate 25.

[0152] In the graph shown in FIG. 6C, B means the angle of the blade plate 25 in the vicinity of the impeller outlet 27 described in FIG. 6A, and Z means the height of the blade plate 25 in the axial direction AD described in FIG. 6B. The solid line indicated by the symbol SL1 shows an example of the shape of the blade plate 25. As shown by the solid line SL1, when the height of the blade plate 25 is at a position significantly lower than position Z1, the angle B of the blade plate 25 is a negative value. As the height of the blade plate 25 increases, the value of the angle B of the blade plate 25 increases, and the value of the angle B changes from a negative value to a positive value. Furthermore, as the height of the blade plate 25 increases, the value of the angle B of the blade plate 25 increases. When the height of the blade plate 25 reaches position Z1, the value of the angle B becomes the highest positive value. Here, the position Z1 corresponds to the second region R2 in the blade plate 25 shown in FIG. 6B. Next, as the height of the blade plate 25 increases, the value of the angle B of the blade plate 25 begins to decrease, and the value of the angle B changes from a positive value to a negative value. Furthermore, as the height of the blade plate 25 increases, the value of the angle B of the blade plate 25 decreases. When the height of the blade plate 25 reaches position Z2, the value of the angle B becomes a negative value. Here, the position Z2 corresponds to the third region R3 in the blade plate 25 shown in FIG. 6B.

[0153] In the present embodiment, the value of the angle B when the height of the blade plate 25 is at position Z1 is a positive value, but the value of the angle B may also be 0 degrees. Also, the value of the angle B when the height of the blade plate 25 is at position Z2 is a negative value, but the value of the angle B may also be 0 degrees. The distribution of the angle between points is not limited to the above-described embodiment.

[0154] That is, regarding the angle B of the blade plate 25 in the second region R2 near the impeller outlet 27, when the angle B of the blade plate 25 is set to 0 degrees with respect to the radial direction RD of the impeller 21, and the angle B of the blade plate 25 is set to a positive value with respect to the rotational direction +R of the impeller 21, the maximum value of the angle B of the blade plate 25 is 0 degrees or a positive value. In particular, the above conditions regarding the angle B of the blade plate 25 are more preferable when the tip portion 41 of the first member 40 is disposed at the maximum position PX.

[0155] Regarding the angle B of the blade 25 in the third region R3 at the impeller outlet 27, when the angle B of the blade 25 is set to 0 degrees with respect to the radial direction RD of the impeller 21 and the angle B of the blade 25 is set to a positive value with respect to the rotation direction +R of the impeller 21, the minimum value of the angle B of the blade 25 is 0 degrees or a negative value. In particular, the above condition regarding the angle B of the blade 25 is more preferable when the tip 41 of the first member 40 is disposed at the maximum position PX.

[0156] <Function and effect> With reference to FIGS. 7A to 7D, the function and effect of the present embodiment will be described. The velocity triangles shown in FIGS. 7A to 7D show the relationship between the fluid FL flowing out from the second region R2 of the impeller 21 and the peripheral velocity (circumferential velocity) of the outer periphery of the impeller 21 when the fluid FL collides with the first member 40 and flows into the third region R3 of the impeller 21 when the first member 40 of the fluid machine protrudes from the shroud wall 31.

[0157] FIG. 7A shows a velocity triangle when the fluid FL flows out from the second region R2 of the impeller outlet 27 in the impeller 21 according to the present embodiment. Reference numeral U2 is the velocity (circumferential velocity) in the rotation direction at the impeller outlet 27. Reference numeral W2 is the velocity at which the fluid FL flows out from the impeller 21 and is the relative velocity of the fluid FL with respect to the impeller 21. In the impeller 21 according to the present embodiment, the maximum value of the angle B in the second region R2 of the blade 25 is a positive value in the vicinity of the impeller outlet 27. Therefore, the relative velocity W2 has a vector directed in the direction in which the angle B becomes a positive value. Reference numeral C2 is the vector sum of the relative velocity W2 and the circumferential velocity U2 and is the absolute velocity of the fluid FL flowing out from the impeller 21.

[0158] FIG. 7B shows a velocity triangle when the fluid FL flowing out from the second region R2 of the impeller outlet 27 according to the present embodiment collides with the first member 40 and the component of the velocity of the fluid FL in the radial direction RD is reversed and the fluid FL flows into the third region R3 of the impeller outlet 27. Reference numeral C 2REis the absolute velocity of the fluid FL that has collided with the first member 40 and reversed its direction. Here, it is assumed that there is no loss from when the fluid FL exits the second region R2 of the impeller 21 until it flows into the third region R3. The fluid FL flows into the third region R3 of the impeller outlet 27 that rotates at the same peripheral speed U2 as when it flowed out from the impeller outlet 27. The relative velocity W of the fluid FL with respect to the impeller 21 2RE is obtained by subtracting the peripheral speed U2 from the absolute velocity C 2RE by vector calculation. As a result, the relative velocity W 2RE shown in FIG. 7B is obtained.

[0159] Here, in the fluid machine according to the present embodiment, the minimum value of the blade angle in the third region R3 near the impeller outlet 27 is a negative value. Therefore, the fluid FL flows into the third region R3 so that the blade angle of the blade plate 25 in the third region R3 near the impeller outlet 27 follows the relative velocity of the inflowing fluid FL. For this reason, the loss when the fluid FL flows into the third region R3 of the impeller outlet 27 can be minimized, and the loss due to recirculation in the third region R3 and the second region R2 can be minimized.

[0160] Therefore, even when the first member 40 protrudes from the shroud wall 31 to decrease or adjust the suction flow rate of the fluid machine, a decrease in efficiency can be suppressed to a minimum. Here, the suction flow rate is equal to the discharge flow rate. Also, the minimum value of the angle of the blade plate 25 in the third region R3 near the impeller outlet 27 is a negative value. For this reason, compared with the case where the angle of the blade plate 25 is a positive value, as described above, the definition of the angle of the blade plate 25 is such that the difference from the angle of the blade plate 25 at the impeller inlet 26 where the angle of the blade plate 25 is a negative value is small. Therefore, the bending of the blade plate 25 in the third region R3 can be suppressed.

[0161] The third region R3 is near the shroud wall 31. Therefore, the distance in the meridian plane of the blade plate 25 is shorter than that in the first region R1 and the second region R2. Note that if the change in the angle of the blade plate 25 is large in a short section, the bend of the blade plate 25 becomes large. When the bend of the blade plate 25 becomes large, so-called separation occurs, such as the flow of the fluid FL not flowing along the blade plate 25, and the efficiency of the impeller 21 decreases. In the impeller 21 according to the present embodiment, the minimum value of the angle of the blade plate 25 in the third region R3 near the impeller outlet 27 is a negative value. For this reason, the efficiency of the impeller 21 does not decrease.

[0162] FIG. 7C shows a velocity triangle when the fluid FL flows out from the second region R2 of the impeller outlet 27 when the angle of the blade plate 25 in the second region R2 near the impeller outlet 27 of the impeller 21 according to the present embodiment is 0. The meaning of the velocity symbol is the same as the meaning of the symbol described above. The fluid FL flowing out from the second region R2 of the impeller outlet 27 flows out at an angle of 0 along the blade plate 25 facing the radial direction RD. Thereby, the absolute velocity C2 shown in FIG. 7C is obtained.

[0163] FIG. 7D shows a velocity triangle when the fluid FL flowing out from the second region R2 of the impeller outlet 27 collides with the first member 40 and the outward component of the velocity of the fluid FL in the radial direction RD is reversed and flows into the third region R3 of the impeller outlet 27 when the angle of the blade plate 25 in the third region R3 near the impeller outlet 27 of the impeller 21 according to the present embodiment is 0. The fluid FL that has collided with the first member 40 and has been reversed has an absolute velocity C 2RE The fluid FL flowing into the third region R3 of the impeller outlet 27 that rotates at the peripheral speed U2 flows in with a relative velocity in the inward radial direction RD. Here, in the fluid machine according to the present embodiment, the minimum value of the blade angle in the third region R3 near the impeller outlet 27 is 0. For this reason, the fluid FL flows into the third region R3 so that the blade angle of the blade plate 25 in the third region R3 near the impeller outlet 27 follows the relative velocity of the inflowing fluid FL. Therefore, when the fluid FL flows into the third region R3 of the impeller outlet 27, the loss can be minimized, and the loss due to the recirculation in the third region R3 and the second region R2 can be minimized.

[0164] Therefore, even when the first member 40 protrudes from the shroud wall 31 to reduce or adjust the suction flow rate of the fluid machine, the decrease in efficiency can be minimized. Here, the suction flow rate is equal to the discharge flow rate. In addition, the minimum value of the angle of the blade plate 25 in the third region R3 near the impeller outlet 27 is 0. For this reason, compared with the case where the angle of the blade plate 25 is a positive value, as described above, the definition of the angle of the blade plate 25 is the same as above, and the difference from the angle of the blade plate 25 at the impeller inlet 26 where the angle of the blade plate 25 is a negative value is small. Therefore, the bending of the blade plate 25 in the third region R3 can be suppressed.

[0165] The third region R3 is near the shroud wall 31. Therefore, the distance in the meridian plane of the blade plate 25 is shorter than that in the first region R1 and the second region R2. If the change in the angle of the blade plate 25 is large in a short section, the bending of the blade plate 25 becomes large. When the bending of the blade plate 25 becomes large, so-called separation occurs, such as the flow of the fluid FL not flowing along the blade plate 25, and the efficiency of the impeller 21 decreases. In the impeller 21 according to the present embodiment, since the minimum value of the angle of the blade plate 25 in the third region R3 near the impeller outlet 27 is 0, the efficiency of the impeller 21 does not decrease.

[0166] As described above, by using the blade plate 25 according to the third embodiment, the effects obtained by the first embodiment can be further enhanced. That is, the generation of the recirculation of the fluid FL in the second region R2 and the third region R3 can be promoted while minimizing the loss. Since the decrease in the flow rate in the fluid machine 10 can be promoted, the decrease in efficiency can be minimized while promoting the decrease or adjustment of the flow rate. Note that the dotted lines DL1 and DL2 shown in FIG. 6C indicate modified examples of the shape of the blade plate 25. The above-described effects can also be obtained in each of the dotted lines DL1 and DL2. In the above description, the case where the first member 40 is used has been described. However, instead of the first member 40, each of the above-described first members 60A to 60J may be used.

[0167] <Fourth Embodiment> <Impeller> Next, the impeller 21 according to the fourth embodiment will be described. Here, the same members as those described with reference to FIGS. 1 to 2B are denoted by the same reference numerals, and the description thereof is omitted or simplified. In FIG. 8A, among the components constituting the fluid machine, the components other than the impeller are omitted.

[0168] The impeller 21 has a partition member 28 facing the shroud wall 31. The partition member 28 has a blade opening 28P. The blade opening 28P is located closer to the impeller inlet 26 than the impeller outlet 27. The partition member 28 is fixed to the blade plate 25, for example. Thereby, the distance between the blade main plate 24 and the partition member 28 is maintained, and the distance between the shroud wall 31 and the partition member 28 is maintained. In particular, the partition member 28 is located at the boundary between the second region R2 and the third region R3 between the blade main plate 24 and the shroud wall 31.

[0169] <Operating Effects> Next, the operating effects of the impeller 21 provided with the partition member 28 will be described. As described above, by adjusting the protrusion amount AP, in the second region R2, the fluid FL flows in the first direction FD. When the fluid FL flowing through the second region R2 collides with the first member, the fluid FL flows in the second direction SD in the third region R3. At this time, the partition member 28 separates the fluid FL flowing through the second region R2 and the fluid FL flowing through the third region R3. Further, the fluid FL flowing through the third region R3 flows from the third region R3 into the second region R2 via the blade opening 28P. Therefore, by providing the partition member 28 on the impeller 21, the flow of the fluid FL flowing through the second region R2 can be promoted, and the flow of the fluid FL flowing through the third region R3 can be promoted. For this reason, the recirculation of the fluid FL in the second region R2 and the third region R3 is promoted. Thereby, the flow rate of the fluid machine can be reduced.

[0170] <Modification of the Fourth Embodiment> Next, with reference to FIG. 8B, a modification of the first member will be described. Here, the same members as those described with reference to FIG. 8A are denoted by the same reference numerals, and the description thereof is omitted or simplified. The impeller 21 shown in FIG. 8B is different from the structure shown in FIG. 8A in terms of the position of the blade opening 28P. In the impeller 21 shown in FIG. 8B, the blade opening 28P is located closer to the impeller inlet 26 than the impeller outlet 27 and is located at the upstream end of the partition member 28. In other words, the blade opening 28P is located at the impeller inlet 26. Even in such a configuration, the partition member 28 can promote the flow of the fluid FL flowing through the second region R2 and can promote the flow of the fluid FL flowing through the third region R3. For this reason, the recirculation of the fluid FL in the second region R2 and the third region R3 is promoted. Thereby, the flow rate of the fluid machine can be reduced.

[0171] In the example shown in FIG. 8B, the blade opening 28P is arranged upstream of the position of the blade opening 28P in FIG. 8A. For this reason, in the first direction FD, the length of the fluid FL flowing in the second region R2 can be increased, and the length of the fluid FL flowing in the third region R3 can be increased. In other words, by adjusting the position of the blade opening 28P, the degree of recirculation of the fluid FL in the second region R2 and the third region R3 can be adjusted.

[0172] <Fifth Embodiment> <Blade Plate> Here, the same members described with reference to FIGS. 1 to 2B are denoted by the same reference numerals, and the description thereof is omitted or simplified. In FIG. 9, among the components constituting the fluid machine, the components other than the impeller are omitted.

[0173] The impeller 21A shown in FIG. 9 has side plates 29. The side plates 29 are joined to the blade plates 25 so as to be separated from the blade main plates 24. The side plates 29 face the shroud wall 31. The impeller 21A having such a configuration is a so-called closed impeller. The impeller 21A can be applied to the above-described first embodiment, second embodiment, and modification. Therefore, effects similar or analogous to those of the first embodiment, second embodiment, and modification can be obtained.

[0174] <Modification of Blade Plate> The impeller 21A shown in FIG. 10A has the partition member 28 described with reference to FIG. 8A. As shown in FIG. 10A, the partition member 28 is disposed between the side plate 29 and the blade main plate 24. Each of the partition member 28 and the side plate 29 is fixed to the blade plate 25, for example. Thereby, the interval between the blade main plate 24 and the partition member 28 is maintained, the interval between the partition member 28 and the side plate 29 is maintained, and the interval between the side plate 29 and the shroud wall 31 is maintained. In particular, the partition member 28 is located at the boundary between the second region R2 and the third region R3 between the blade main plate 24 and the shroud wall 31.

[0175] In the impeller 21A, the partition member 28 separates the fluid FL flowing in the second region R2 from the fluid FL flowing in the third region R3. Further, the fluid FL flowing in the third region R3 flows from the third region R3 into the second region R2 via the blade opening 28P. Therefore, the flow of the fluid FL flowing in the second region R2 can be promoted, and the flow of the fluid FL flowing in the third region R3 can be promoted. Therefore, the recirculation of the fluid FL in the second region R2 and the third region R3 is promoted. Thereby, the flow rate of the fluid machine can be reduced.

[0176] The impeller 21A shown in FIG. 10B has the partition member 28 described with reference to FIG. 8B. Even in such a configuration, the partition member 28 can promote the flow of the fluid FL flowing through the second region R2 and can promote the flow of the fluid FL flowing through the third region R3. For this reason, the recirculation of the fluid FL in the second region R2 and the third region R3 is promoted. Thereby, the flow rate of the fluid machine can be decreased.

[0177] <Sixth Embodiment> <Thermal Cycle System> The fluid machine 10 according to the first to fifth embodiments described above can be applied to a thermal cycle system. With reference to FIGS. 11 and 12, a thermal cycle system including the fluid machine 10 will be described. The thermal cycle system 70 includes a compressor 71, a condenser 72, an expansion valve 73, an evaporator 74, a first supply pump 75, and a second supply pump 76. The thermal cycle system 70 is, for example, a refrigerator or a heat pump.

[0178] The compressor 71 compresses the working fluid vapor A into a high-temperature and high-pressure working fluid vapor B. The compressor 71 is an example of the fluid machine 10 described above. The working fluid is, for example, water, hydrocarbon, fluorine-based substance, etc. The fluorine-based substance is, for example, freon, etc. The condenser 72 cools the working fluid vapor B discharged from the compressor 71 and liquefies it into a low-temperature and high-pressure working fluid C. The condenser 72 is, for example, a heat exchanger. The shape, type, structure, etc. of the heat exchanger are not particularly limited. The expansion valve 73 expands the working fluid C discharged from the condenser 72 into a low-temperature and low-pressure working fluid D. The evaporator 74 heats the working fluid D discharged from the expansion valve 73 into a high-temperature and low-pressure working fluid vapor A. The evaporator 74 is, for example, a heat exchanger. The shape, type, structure, etc. of the heat exchanger are not particularly limited. The first supply pump 75 supplies the load fluid E to the evaporator 74. Here, the load fluid E is, for example, water, antifreeze, air, etc. The second supply pump 76 supplies the fluid FL to the condenser 72.

[0179] As described above, the embodiments and modifications of the present invention have been explained, but it should be understood that these are exemplary of the present invention and should not be considered as limiting. Additions, omissions, substitutions, and other changes can be made without departing from the scope of the present invention. Therefore, the present invention should not be regarded as being limited by the foregoing description, but is limited by the claims.

Explanation of reference numerals

[0180] 10... Fluid machine, 20... Rotating structure, 21, 21A... Impeller, 22... Rotating shaft, 23... Support member, 24... Impeller main plate, 25... Impeller plate, 26... Impeller inlet, 27... Impeller outlet, 28... Partition member, 28P... Impeller opening, 29... Side plate, 30... Casing, 31... Shroud wall, 32... Main plate side wall, 33... Inlet, 34... Outlet, 35... First member accommodation groove, 36... Second member accommodation groove, 37... Accommodation part, 41, 60X... Tip part, 42... Division part, 43... Gap part, 50, 50A, 50B, 50C, 50D, 50E, 50F, 50G, 50H... Second member, 50AE... End face, 50AF, 50AS, 50EF, 50FF... Plate member, 50BE... End face, 50BF... Elastic member, 50BS... Elastic member, 50CL... Downstream protrusion, 50CU... Upstream protrusion, 50DA, 50FA... Shaft part, 51... Flow area, 40, 40A, 60A, 60B, 60C, 60D, 60E, 60F, 60G, 60H, 60I, 60J... First member, 61... Protrusion part, 62... Base part, 62B... Bottom part, 62C... Curved surface, 62D... Base downstream surface, 62F... First base, 62K... Inclined surface, 62P... Through hole, 62R... Depression part, 62S... Second base, 62U... Base upstream surface, 63... First extending part, 64... Second extending part, 65... Accommodation area, 70... Thermal cycle system, 71... Compressor, 72... Condenser, 73... Expansion valve, 74... Evaporator, 75... First supply pump, 76... Second supply pump, D1... First drive part, D2... Second drive part, DR... Downstream side area, FL... Fluid, FP... Flow path, R1... First area, R2... Second area, R3... Third area, UR... Upstream side area, US... Upstream side, WL... Inner wall

Claims

1. A rotating structure having an impeller with a blade main plate and a blade plate, and a rotating shaft that rotatably supports the impeller, a casing that rotatably houses the rotating structure, and has a shroud wall facing the blade plate, a main plate side wall facing the blade main plate, an inlet through which fluid flows in, and an outlet through which the fluid flows out, a flow path through which at least a part of the fluid flows in a first direction from the inlet toward the outlet, a first member provided downstream of the impeller between the main plate side wall and the shroud wall, being relatively movable with respect to the shroud wall, and having a variable protruding amount with respect to the flow path in the vicinity of the downstream end of the impeller, a second member disposed on the shroud wall upstream of the impeller in the first direction, and capable of adjusting the flow of the fluid along the shroud wall toward the impeller in the first direction, and a fluid machine.

2. The second member has an upstream surface located on the upstream side of the second member and a downstream surface located on the downstream side of the second member, and the second member is configured to reduce the flow rate of the fluid flowing toward the downstream side of the downstream surface rather than the flow rate of the fluid flowing toward the upstream surface among the fluid flowing along the shroud wall toward the impeller. The fluid machine according to Claim 1.

3. In the radial direction of the flow path in a cross section of the flow path parallel to the direction orthogonal to the first direction, the second member is relatively movable with respect to the shroud wall, and by moving the second member with respect to the shroud wall, the second member is configured to reduce the flow rate of the fluid in the vicinity of the shroud wall. The fluid machine according to Claim 2.

4. The second member has an elastic member that forms a part of the shroud wall, and by deforming the elastic member, the second member is configured to reduce the flow rate of the fluid in the vicinity of the shroud wall. The fluid machine according to Claim 2.

5. The second member has an upstream protrusion disposed on the inner wall of the flow path on the upstream side in the first direction, and a downstream protrusion disposed on the inner wall of the flow path on the downstream side of the upstream protrusion in the first direction, and In the circumferential direction of the flow path in a cross-section of the flow path parallel to the direction orthogonal to the first direction, the upstream protrusion and the downstream protrusion are rotatable relative to each other, By the relative rotation of the upstream protrusion and the downstream protrusion, the second member is configured to reduce the flow rate of the fluid in the vicinity of the shroud wall. The fluid machine according to claim 2.

6. The second member has a shaft portion extending in a direction intersecting the radial direction of the flow path in a cross-section of the flow path parallel to the direction orthogonal to the first direction and in a direction intersecting the first direction, By rotating the second member around the shaft portion, the second member is configured to reduce the flow rate of the fluid in the vicinity of the shroud wall. The fluid machine according to claim 2.

7. The second member has a shaft portion extending in the radial direction of the flow path in a cross-section of the flow path parallel to the direction orthogonal to the first direction, By rotating the second member around the shaft portion, the second member is configured to reduce the flow rate of the fluid in the vicinity of the shroud wall. The fluid machine according to claim 2.

8. The impeller has an impeller inlet located upstream of the impeller in the flow path and communicating with the flow path, By adjusting the distance between the second member and the impeller inlet in the first direction, the second member is configured to reduce the flow rate of the fluid in the vicinity of the shroud wall. The fluid machine according to claim 2.

9. A rotating structure having an impeller having an impeller main plate and impeller vanes, and a rotating shaft that rotatably supports the impeller, A casing that rotatably houses the rotating structure and has a shroud wall facing the impeller vanes, a main plate side wall facing the impeller main plate, an inlet through which fluid flows in, and an outlet through which the fluid flows out, A flow path through which at least a part of the fluid flows in a first direction from the inlet toward the outlet, A first member provided downstream of the impeller between the main plate side wall and the shroud wall, movable relative to the shroud wall, having a variable protrusion amount with respect to the flow path in the vicinity of the downstream end of the impeller, and having a protrusion portion protruding toward the upstream side in the first direction, having a fluid machine.

10. When viewed in the axial direction in which the rotation axis extends, the first member is disposed at a position radially away from the rotation axis. The fluid machine according to claim 1 or claim 9.

11. When viewed in the axial direction, the first member has an annular shape. The fluid machine according to claim 10.

12. When viewed in the axial direction, the first member has a circular shape, an oval shape, an elliptical shape, or a polygonal shape. The fluid machine according to claim 11.

13. When viewed in the axial direction, the first member has a non-annular shape. The fluid machine according to claim 10.

14. When viewed in the axial direction, the first member has a plurality of divided portions arranged radially from the rotation axis, and the plurality of divided portions are spaced apart along the circumferential direction of the first member. The fluid machine according to claim 13.

15. The first member has the plurality of divided portions and a gap portion where the plurality of divided portions are not formed in the circumferential direction. Assuming that the area ratio of the first member in the annular shape where the gap portion is not formed is 1.0 when viewed in the axial direction, the total area ratio of the gap portions formed along the circumferential direction is 0.2 or less when viewed in the axial direction. The fluid machine according to claim 14.

16. The first member has a protrusion protruding toward the upstream side in the first direction and a base extending in the extending direction in which the first member extends. The protrusion has a first extending portion facing the main board side wall. The first extending portion is provided in a part of the base and extends from the base toward the impeller. The fluid machine according to claim 1 or claim 9.

17. The first member has a second extending portion facing the first extending portion. The base has an accommodation region accommodated in the shroud wall. The second extending portion is provided in the accommodation region. The fluid machine according to claim 16.

18. The first member has a protrusion protruding toward the upstream side in the first direction and a base extending in the extending direction in which the first member extends. The base has a base upstream surface facing the impeller. The protrusion has a recess provided on the base upstream surface. The fluid machine according to claim 1 or claim 9.

19. The cross-sectional shape of the recess has a shape having at least one of a curved portion and an angular portion. The fluid machine according to claim 18.

20. The first member has a base extending in the extending direction in which the first member extends, and the base is the base upstream surface facing the impeller; the base downstream surface on the side opposite to the base upstream surface; a through hole provided in the base so as to extend from the base upstream surface toward the base downstream surface; having the fluid machine according to claim 1 or claim 9.

21. The first member has a tip portion located at the most distal end among the portions of the first member protruding into the flow path, The tip portion can be arranged at a minimum position where the first member is accommodated inside the shroud wall and the protruding amount of the first member is minimized, a maximum position where the protruding amount of the first member protruding from the shroud wall toward the flow path is maximized, and an intermediate position between the maximum position and the minimum position. the fluid machine according to claim 1 or claim 9.

22. When the tip portion is arranged at the minimum position, the fluid flows through the flow path from the inlet toward the outlet without colliding with the first member. the fluid machine according to claim 21.

23. When the tip portion is arranged at the maximum position or the intermediate position, a first region, a second region, and a third region are formed in the flow path between the impeller and the shroud wall. In the first region, the fluid flows through the flow path from the inlet toward the outlet without colliding with the first member. In the second region, the fluid flows toward the first member and collides with the first member. In the third region, the fluid that has collided with the first member flows in a second direction opposite to the first direction. the fluid machine according to claim 21.

24. The impeller has an impeller outlet located on the downstream side of the impeller in the flow path, The impeller has an impeller inlet located on the upstream side of the impeller in the flow path and communicating with the flow path, The impeller has a partition member facing the shroud wall, The partition member has a blade opening located closer to the impeller inlet than the impeller outlet, The partition member is located at the boundary between the second region and the third region, The fluid flows from the third region into the second region through the blade opening. the fluid machine according to claim 23.

25. The impeller has an impeller outlet located on the downstream side of the impeller in the flow path, Regarding the angle of the blade in the second region near the impeller outlet, When the angle of the blade plate is set to 0 degrees with respect to the radial direction of the impeller and the angle of the blade plate is set to a positive value with respect to the rotational direction of the impeller, the maximum value of the angle of the blade plate is 0 degrees or a positive value. The fluid machine according to claim 23.

26. The impeller has an impeller outlet located on the downstream side of the impeller in the flow path. Regarding the angle of the blade plate in the third region near the impeller outlet, when the angle of the blade plate is set to 0 degrees with respect to the radial direction of the impeller and the angle of the blade plate is set to a positive value with respect to the rotational direction of the impeller, the minimum value of the angle of the blade plate is 0 degrees or a negative value. The fluid machine according to claim 23.

27. The first member has a base portion extending in the extending direction in which the first member extends. The base portion has a base upstream surface facing the impeller, a base downstream surface on the side opposite to the base upstream surface, and a through hole provided in the base portion so as to extend from the base upstream surface toward the base downstream surface. has A part of the fluid flowing through the flow path flows through the through hole in the second direction opposite to the first direction, reaches the base upstream surface, and merges with the fluid flowing in the second region. The fluid machine according to claim 23.

28. By the fluid flowing through the through hole in the second direction and the fluid flowing in the second region merging, a merged fluid is generated on the base upstream surface. The merged fluid accelerates the flow of the fluid in the third region. The fluid machine according to claim 27.

29. It is connected to the first member and has a first drive unit that relatively moves the first member with respect to the shroud wall. The fluid machine according to claim 1 or claim 9.

30. It is connected to the second member and has a second drive unit that relatively moves the second member with respect to the shroud wall. The fluid machine according to claim 1.

31. It is connected to the first member and has a first drive unit that relatively moves the first member with respect to the shroud wall. The first drive unit and the second drive unit move the first member and the second member so that the first member and the second member are synchronized with each other. The fluid machine according to claim 30.

32. It has a drive unit that moves the first member and the second member. The drive unit is connected to the first member and relatively moves the first member with respect to the shroud wall. The drive unit is connected to the second member and relatively moves the second member with respect to the shroud wall. The drive unit moves the first member and the second member so that the first member and the second member are synchronized with each other. The fluid machine according to claim 1.

33. The impeller has side plates joined to the blade plates so as to be spaced apart from the blade main plates. The side plates face the shroud wall. The fluid machine according to claim 1 or claim 9.

34. A thermal cycle system comprising the fluid machine according to claim 1 or claim 9. Thermal cycle system.

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