JP5558183B2 - Turbo machine - Google Patents

Description

  The present invention relates to a turbo machine, and is applied to a turbo pump, a turbo blower, a turbo compressor, or the like to reduce the loss of the turbo machine and improve the performance.

  As the turbo machine, there are a turbo-type pump that discharges after increasing the pressure of liquid (water, etc.), and a turbo-type blower or a turbo-type compressor that discharges after increasing the pressure of gas (air, etc.).

Here, a conventional configuration of a mixed flow pump, which is a kind of turbo pump, will be described with reference to FIGS.
The mixed flow pump shown in FIG. 7 is an open type, that is, a mixed flow pump that does not have a shroud at the blade tip of the impeller. The mixed flow pump shown in FIGS. 8 and 9 is a closed type, that is, a mixed flow pump having a shroud at the blade tip of the impeller.

FIG. 7 is a meridional view showing the open-type mixed flow pump 1, in which the left side of FIG. 7 is the suction side and the right side is the discharge side, and the flow of liquid (water or the like) is depicted by arrows.
An impeller (impeller) 20 is attached to the rotating shaft 10 of the mixed flow pump 1. More specifically, the rotating shaft 10 is attached to the hub 21 of the impeller 20, and the rotating shaft 10 and the hub 21 are fixed. The impeller 20 has a plurality of blades 22, and the blades 22 are arranged at a plurality of locations along the circumferential direction. Each blade 22 extends while curving along the flow direction of the liquid, and also extends in the radial direction.

The casing 30 is disposed on the outer peripheral side of the impeller 20, and a slight gap (chip clearance) is provided between the tip of the blade 22 (tip portion: tip in the radial direction) and the inner peripheral surface of the casing 30. Provided.
A diffuser vane 40 is disposed on the discharge side of the impeller 20 (downstream with respect to the liquid flow direction). The diffuser vane 40 is fixedly installed on the inner peripheral surface of the casing 30.

  In such a mixed flow pump 1, the rotational force of a drive source (not shown) is transmitted to the impeller 20 by the rotating shaft 10, and the impeller 20 rotates to increase the pressure of the liquid sucked from the suction side and discharge it. Can be pumped from the side.

  FIG. 8 is a meridional view showing a closed-type mixed flow pump 1A. The left side of FIG. 8 is the suction side, the right side is the discharge side, and the flow of liquid (water, etc.) is depicted by arrows. FIG. 9 is an external view showing the impeller 20 and the shroud 50 with the casing 30 of the closed mixed flow pump 1A omitted.

  An impeller (impeller) 20 is attached to the rotating shaft 10 of the mixed flow pump 1A. More specifically, the rotating shaft 10 is attached to the hub 21 of the impeller 20, and the rotating shaft 10 and the hub 21 are fixed. The impeller 20 has a plurality of blades 22, and the blades 22 are arranged at a plurality of locations along the circumferential direction. Each blade 22 extends while curving along the flow direction of the liquid, and also extends in the radial direction.

The casing 30 is disposed on the outer peripheral side of the impeller 20.
A diffuser vane 40 is disposed on the discharge side of the impeller 20 (downstream with respect to the liquid flow direction). The diffuser vane 40 is fixedly installed on the inner peripheral surface of the casing 30.

The shroud 50 is formed in a cylindrical shape, is concentric with the rotating shaft 10 and the impeller 20, and is disposed in a state of surrounding the tip portion (tip portion: tip portion in the radial direction) of each blade 22. Yes. Moreover, the inner peripheral surface of the shroud 50 and the tip of each blade 22 are connected.
In this example, the front edge of the shroud 50 with respect to the length Lb from the front edge portion (upstream side with respect to the liquid flow direction) to the rear edge portion (downstream side with respect to the liquid flow direction) of each blade 22. The length Ls from the part to the rear edge is longer. In other words, a portion from the front edge portion to the rear edge portion of the front end portion of each blade 22 is surrounded by the inner peripheral surface of the shroud 50.
In a closed pump, Lb ≦ Ls is generally satisfied.

  On the inner peripheral surface of the casing 30, a concave groove 31 is formed in a ring shape corresponding to the arrangement position of the shroud 50, and the shroud 50 enters the concave groove 31. That is, the shroud 50 is disposed in the concave groove 31 so that the shroud 50 is positioned on the outer peripheral side that is out of the liquid flow path.

  A gap is formed between the shroud 50 and the casing 30, and in particular, on the upstream side (left side in FIG. 8), a seal portion Se is formed in which the gap between the shroud 50 and the casing 30 is narrowed.

  In such a mixed flow pump 1A, the rotational force of the drive source (not shown) is transmitted to the impeller 20 by the rotating shaft 10, and the impeller 20 rotates to compress the liquid sucked from the suction side and discharge it. Can be pumped from the side.

  Incidentally, in the past, in consideration of performance and effects, a closed type was used for centrifugal pumps, and an open type was used for mixed flow pumps and axial flow pumps.

JP2007-291874A Special table 2003-525172 JP 2005-315216 A

  In the open mixed flow pump 1 shown in FIG. 7, as shown in FIG. 10, a loss Lo <b> 1 due to the leakage flow F <b> 1 from the tip of the blade 22 occurs. The leakage flow F1 is such that the liquid flows from the front surface of the blade 22 toward the back surface (the blade surface on the side where the liquid is low pressure) from the abdominal surface of the blade 22 (the blade surface on the side where the liquid is high pressure). This is caused by flowing through a gap between the casing 30 and the casing 30.

In the closed mixed flow pump 1A shown in FIGS. 8 and 9, since there is the shroud 50, the leakage flow F1 does not occur, and therefore the loss Lo1 does not occur.
However, in the closed-type mixed flow pump 1A, the gap between the outer peripheral surface of the shroud 50 and the inner peripheral surface of the casing 30 enters from the rear edge side of the shroud 50 and flows out from the front edge side of the shroud 50 through the seal portion Se. A loss Lo2 due to the circulating leakage flow F2 occurs. The leakage flow F2 is caused by a pressure difference between the liquid at the rear edge side of the shroud 50 and the liquid at the front edge side at a low pressure.
Further, in the closed type mixed flow pump 1 </ b> A, a loss Lo <b> 3 due to viscous friction of the liquid that occurs between the outer peripheral surface of the shroud 50 and the inner peripheral surface of the casing 30 occurs.

  As described above, in the prior art, large loss Lo1 to Lo3 occurs regardless of whether the type is an open type or a closed type, which hinders improvement in pump performance. Particularly in large pumps for power plants and public use, the losses Lo1 to Lo3 are large, which hinders improvement in pump performance.

  In addition, not only turbo pumps but also turbo blowers or turbo compressors have similar problems.

  An object of the present invention is to provide a turbomachine that has improved performance by reducing loss as much as possible in view of the above-described prior art.

The configuration of the present invention for solving the above problems is as follows.
By rotating an impeller with blades arranged at multiple locations along the circumferential direction, a turbomachine that pumps fluid, or an impeller with blades disposed at multiple locations along the circumferential direction due to the pressure difference of the fluid rotates to extract power In turbomachinery,
Concentric with the impeller and disposed in a state surrounding the tip of each blade, and includes a cylindrical tip ring whose inner peripheral surface is joined to the tip of the blade,
The length from the leading edge of the tip ring to the trailing edge of the tip ring along the leading edge of the blade becomes shorter than the length from the leading edge to the trailing edge of the tip of the blade. and,
The outer peripheral surface of the tip ring and the portion of the tip of the blade that is not covered with the tip ring are flush with each other,
A cross-sectional shape of the tip ring is a streamlined shape in which a front edge side and a rear edge side are thin, and a central portion along a flow direction of the fluid is thick .

The configuration of the present invention is as follows.
The length from the front edge of the tip of the blade to the rear edge is Lb, and the length from the front edge of the tip ring to the rear edge of the tip ring along the tip of the blade is Lt. sometimes,
0.1Lb <Lt <0.8Lb
Or
0.3Lb <Lt <0.5Lb
It is characterized by becoming.

The configuration of the present invention is as follows.
By rotating an impeller with blades arranged at multiple locations along the circumferential direction, a turbomachine that pumps fluid, or an impeller with blades disposed at multiple locations along the circumferential direction due to the pressure difference of the fluid rotates to extract power In turbomachinery,
At the tip of each blade, provided with a chip protruding plate that protrudes along the circumferential direction from the tip of the blade toward the tip of the adjacent blade,
The chip protruding plates face each other without contact,
The length from the front edge of the tip protruding plate to the rear edge of the tip protruding plate along the tip of the blade is longer than the length from the leading edge to the rear edge of the tip of the blade. It ’s getting shorter ,
Each of the chip protruding plates is characterized in that the amount of protrusion on the abdominal surface side is larger than the amount of protrusion on the back surface side .

The configuration of the present invention is as follows.
The length from the leading edge of the tip of the blade to the trailing edge is Lb, and the length from the leading edge of the tip protruding plate to the trailing edge of the tip protruding plate along the tip of the blade is Lt. And when
0.1Lb <Lt <0.8Lb
Or
0.3Lb <Lt <0.5Lb
It is characterized by becoming.

  According to the present invention, since the tip ring and the tip protruding plate are provided, the total loss including the loss due to the leakage flow from the tip of the blade, the loss due to the circulating leakage flow, and the loss due to the viscous friction of the fluid is reduced. This can reduce the efficiency of the turbomachine.

The meridian view which shows the mixed flow pump which concerns on Example 1 of this invention. In Example 1, the external view which shows an impeller and a tip ring in the state which abbreviate | omitted the casing. The characteristic view which shows the relationship between ratio Lt / Lb of the length Lt of a tip ring and the length Lb of a blade | wing tip part, and loss Lo1, Lo2, Lo3. The meridian view which shows the mixed flow pump which concerns on Example 2 of this invention. In Example 2, the external view which shows an impeller and a chip | tip protrusion board in the state which abbreviate | omitted the casing. FIG. 6 is an AA arrow view of FIG. 5. The meridian view showing an open type conventional mixed flow pump. The meridional view showing a closed mixed flow pump. FIG. 3 is an external view showing an impeller and a shroud in a state where a casing is omitted in a conventional closed flow pump. Explanatory drawing which shows the loss by the leakage flow from a blade | wing front-end | tip part.

  Hereinafter, embodiments of the present invention will be described in detail based on examples.

  FIG. 1 is a meridional view showing a mixed flow pump 101 according to Embodiment 1 of the present invention. The left side of FIG. 1 is a suction side, the right side is a discharge side, and the flow of liquid (water, etc.) is drawn by arrows. ing. FIG. 2 is an external view showing the impeller 120 and the tip ring 150 with the casing 130 omitted.

  An impeller (impeller) 120 is attached to the rotating shaft 110 of the mixed flow pump 101. More specifically, the rotating shaft 110 is attached to the hub 121 of the impeller 120, and the rotating shaft 110 and the hub 121 are fixed. The impeller 120 has a plurality of blades 122, and the blades 122 are arranged at a plurality of locations along the circumferential direction. Each blade 122 extends while curving along the flow direction of the liquid, and also extends in the radial direction.

The casing 130 is disposed on the outer peripheral side of the impeller 120.
A diffuser vane 140 is disposed on the discharge side of the impeller 120 (downstream with respect to the liquid flow direction). The diffuser vane 140 is fixedly installed on the inner peripheral surface of the casing 130.

  The tip ring 150 is formed in a cylindrical shape, is concentric with the rotating shaft 110 and the impeller 120, and is disposed so as to surround the tip portion (tip portion: radial tip portion) of each blade 122. ing. In addition, the inner peripheral surface of the tip ring 150 and the tip of each blade 122 are joined.

The tip ring 150 and the impeller 120 (blade 122) may be configured integrally or as separate bodies.
In the case of an integral structure, the tip ring 150 and the impeller 120 blades 122 are integrally formed by casting, cutting, or the like. In this case, it is preferable to provide an R-shaped fillet at the corner between the tip ring 150 and the impeller 120 and increase the strength.
When configured separately, the inner peripheral surface of the tip ring 150 and the tip of the blade 122 are joined by welding, screwing, or the like.

Here, the dimensions of the tip ring 150 will be described.
The length from the leading edge (upstream with respect to the liquid flow direction) to the trailing edge (downstream with respect to the liquid flow direction) of the tip of each blade 122 is Lb. If the length reaching the rear edge of the tip ring 150 along the tip of the tip is Lt,
0.1Lb <Lt <0.8Lb
More preferably,
0.3Lb <Lt <0.5Lb
It is said.
Although details will be described later, by doing so, the loss can be reduced and the performance of the mixed flow pump 101 can be improved.

In this example, the outer peripheral surface of the tip ring 150 and the portion of the tip end portion of the blade 122 that is not covered with the tip ring 150 are smoothly connected so that there is no level difference. Further, the cross-sectional shape of the tip ring 150 is a so-called streamline type in which the front edge side and the rear edge side are thin and the central portion along the liquid flow direction is thick.
In this way, the outer peripheral surface of the tip ring 150 and the tip of the blade 122 are flush with each other, and the cross-sectional shape of the tip ring 150 is a smooth streamline type, so that even if the tip ring 150 is provided, the liquid flow can be maintained. It is smooth so that separation vortices and disturbances can be reduced as much as possible.

  The thickness of the tip ring 150 in the radial direction is made thin enough to satisfy the strength of the tip ring 150 itself. Regarding the circumferential direction, the tip ring 150 may have the same cross-sectional shape or may be changed.

In this example, the tip ring 150 is disposed on the upstream side of the blades 122 with respect to the liquid flow direction, but may be disposed on the center side or the downstream side.
The tip ring 150 is arranged at an optimum position in consideration of the load portion of the blade 122, the length Lt of the tip ring 150, and the like. For example, the tip ring 150 is disposed in a portion where the blade 122 is heavily loaded.

  The tip ring 150 can also be arranged so that a concave groove is formed on the inner peripheral surface of the casing 130 corresponding to the arrangement position of the tip ring 150 and the chip ring 150 enters the concave groove.

  In the mixed flow pump 101 having the above-described configuration, the rotational force of a drive source (not shown) is transmitted to the impeller 120 by the rotating shaft 110, and the impeller 120 rotates to compress the liquid sucked from the suction side. Thus, it can be pumped from the discharge side.

Next, functions and effects of the mixed flow pump 101 according to the first embodiment will be described.
In this mixed flow pump 101, a part of the tip of the blade 122 is covered with the tip ring 150. For this reason, the loss Lo1 due to the leakage flow occurs only in the portion of the tip end portion of the blade 122 that is not covered with the tip ring 150. For this reason, the loss Lo1 due to the leakage flow is reduced.
Further, since the length Lt of the tip ring 150 is short, the loss Lo2 due to the circulating leakage flow and the loss Lo3 due to the viscous friction of the liquid are also reduced. In particular, in the case of the mixed flow pump as in the present embodiment, when the tip ring 150 is arranged on the upstream side in the liquid flow direction, the diameter of the tip ring 150 is made smaller than when the tip ring 150 is arranged on the downstream side. Accordingly, the peripheral speed is reduced accordingly, and the loss Lo3 due to the viscous friction of the liquid can be reduced more effectively.

FIG. 3 shows the relationship between the ratio Lt / Lb between the length Lt of the tip ring 150 and the length Lb of the tip of the blade 122 and the losses Lo1, Lo2, Lo3.
In FIG. 3, Lt / Lb is 0 when the tip ring 150 is not disposed (that is, the same state as the conventional open type), and Lt / Lb is 1 when the tip ring 150 causes the tip portion of the blade 122. A state in which everything from the front edge side to the rear edge side is covered (that is, the same state as a closed type in which a conventional shroud is arranged) is shown.

  In FIG. 3, the dotted line indicates the characteristic of the loss Lo1 due to the leakage flow, the alternate long and short dash line indicates the loss characteristic obtained by adding the loss Lo2 due to the circulating leakage flow and the loss Lo3 due to the viscous friction of the liquid, and the solid line indicates the loss. Loss characteristics including Lo1, loss Lo2, and loss Lo3 are shown.

As can be seen from the characteristics of the solid line in FIG. 3, the length from the front edge portion to the rear edge portion of the tip portion of each blade 122 is Lb, and the tip extends from the front edge portion of the tip ring 150 to the tip portion of the blade 122. If the length to the rear edge of the ring 150 is Lt,
0.1Lb <Lt <0.8Lb
More preferably,
0.3Lb <Lt <0.5Lb
Thus, the loss can be effectively reduced.
Since loss can be reduced in this way, the efficiency of the mixed flow pump 101 can be improved.

Next, a mixed flow pump 101A according to a second embodiment of the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the part which performs the same function as Example 1, and the overlapping description is abbreviate | omitted.
4 is a meridional view showing the mixed flow pump 101A, FIG. 5 is an external view showing the impeller 120 and the tip protruding plate 151 in a state where the casing 130 is omitted, and FIG. 6 is a view taken along arrows AA in FIG. FIG.

In the second embodiment, a curved chip projecting plate 151 is formed in the upstream portion of the tip portion of the blade 122 so as to project along the circumferential direction toward the tip portion of the adjacent blade 122. As shown in FIGS. 4 to 6, the protruding direction of the tip protruding plate 151 is directed toward the tip of the adjacent blade 122 on one side even if it is directed toward the tip of the adjacent blade 122 on both sides. Also good. When projecting to both sides, the projecting amount on both sides may be equal or uneven.
In addition, the adjacent chip projecting plates 151 are opposed to each other with no gap therebetween.

  The tip protruding plate 151 and the impeller 120 (blade 122) may be configured integrally or separately.

The tip projecting plate 151 is formed at the tip of each blade 122, and a plurality of adjacent chip projecting plates 151 are arranged in a circle in the circumferential direction, so that substantially the same effect as the tip ring used in the first embodiment is obtained. Play.
In order to efficiently achieve such an effect, the length from the front edge portion to the rear edge portion of the front end portion of each blade 22 is Lb, and the front edge portion of the tip protruding plate 151 is extended along the front end portion of the blade 22. If the length to the rear edge of the chip protruding plate 151 is Lt,
0.1Lb <Lt <0.8Lb
More preferably,
0.3Lb <Lt <0.5Lb
It is good to do.

  Moreover, if the protrusion amount on the ventral surface side of the blade 22 is increased in the tip protruding plate 151, the leakage flow over the tip of the blade 122 from the abdominal surface side which is the high pressure side toward the back side which is the low pressure side is effectively prevented. This can reduce the loss Lo1.

In the example shown in FIGS. 4 to 6, the tip protruding plate 151 is formed in the upstream portion of the tip end portion of the blade 122, but depending on the load distribution of the blade 122, etc. Of these, the tip protrusion plate 151 may be formed on the middle stream side portion or the downstream side portion.
Further, as a countermeasure against erosion, the corner portion of the chip protruding plate 151 should be rounded, and by rounding it can be made insensitive to changes in the liquid flow direction.

In each of the above embodiments, the present invention is applied to a turbo pump, but the present invention can also be applied to a turbo blower or a turbo compressor.
Moreover, although it demonstrated using the liquid as a fluid, gas may be sufficient.

INDUSTRIAL APPLICABILITY The present invention relates to a turbo-type pump, a turbine, a pump turbine, a compressor, a fan, and a blower that take out power by rotating impellers (impellers) arranged at a plurality of locations along the circumferential direction due to a pressure difference (drop) of fluid. Can be applied to.
Further, the present invention can be applied to a mixed flow type or axial flow type turbo machine among the turbo machines, and also to a centrifugal type turbo machine by disposing a tip ring at the inlet of the impeller.

1, 1A, 101, 101A Mixed flow pump 10, 110 Rotating shaft 20, 120 Impeller (impeller)
21, 121 Hub 22, 122 Blade 30, 130 Casing 31 Groove 40, 140 Diffuser vane 50 Shroud 150 Tip ring 151 Tip protruding plate Se Seal part
Loss of Lo1, Lo2, Lo3

Claims (6)

By rotating an impeller with blades arranged at multiple locations along the circumferential direction, a turbomachine that pumps fluid, or an impeller with blades disposed at multiple locations along the circumferential direction due to the pressure difference of the fluid rotates to extract power In turbomachinery,
Concentric with the impeller and disposed in a state surrounding the tip of each blade, and includes a cylindrical tip ring whose inner peripheral surface is joined to the tip of the blade,
The length from the leading edge of the tip ring to the trailing edge of the tip ring along the leading edge of the blade becomes shorter than the length from the leading edge to the trailing edge of the tip of the blade. and,
The outer peripheral surface of the tip ring and the portion of the tip of the blade that is not covered with the tip ring are flush with each other,
The turbomachine is characterized in that the tip ring has a thin streamline shape at the front edge side and the rear edge side and a thick central part along the fluid flow direction . In claim 1,
The length from the front edge of the tip of the blade to the rear edge is Lb, and the length from the front edge of the tip ring to the rear edge of the tip ring along the tip of the blade is Lt. sometimes,
0.1Lb <Lt <0.8Lb
A turbomachine characterized by In claim 1,
The length from the front edge of the tip of the blade to the rear edge is Lb, and the length from the front edge of the tip ring to the rear edge of the tip ring along the tip of the blade is Lt. sometimes,
0.3Lb <Lt <0.5Lb
A turbomachine characterized by By rotating an impeller with blades arranged at multiple locations along the circumferential direction, a turbomachine that pumps fluid, or an impeller with blades disposed at multiple locations along the circumferential direction due to the pressure difference of the fluid rotates to extract power In turbomachinery,
At the tip of each blade, provided with a chip protruding plate that protrudes along the circumferential direction from the tip of the blade toward the tip of the adjacent blade,
The chip protruding plates face each other without contact,
The length from the front edge of the tip protruding plate to the rear edge of the tip protruding plate along the tip of the blade is longer than the length from the leading edge to the rear edge of the tip of the blade. It ’s getting shorter ,
The turbomachinery characterized in that each of the chip protruding plates has a protrusion on the ventral surface side larger than a protrusion on the rear surface side . In claim 4 ,
The length from the leading edge of the tip of the blade to the trailing edge is Lb, and the length from the leading edge of the tip protruding plate to the trailing edge of the tip protruding plate along the tip of the blade is Lt. And when
0.1Lb <Lt <0.8Lb
A turbomachine characterized by In claim 4 ,
The length from the leading edge of the tip of the blade to the trailing edge is Lb, and the length from the leading edge of the tip protruding plate to the trailing edge of the tip protruding plate along the tip of the blade is Lt. And when
0.3Lb <Lt <0.5Lb
A turbomachine characterized by

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