JP5905517B2 - Impeller - Google Patents

Description

  The present invention relates to an impeller including a disk-like disk that is rotatably attached to a rotating shaft, and a plurality of blades that protrude from the surface of the disk and that are provided in the circumferential direction.

  In a centrifugal compressor that compresses gas using centrifugal force, an impeller having a plurality of blade-like blades provided in a circumferential direction on the surface of a disk-like disk is provided in a plurality of stages along a rotation axis. In this centrifugal compressor, as the rotating shaft rotates, gas passes through a flow path formed by a casing that houses the impeller and the blade, and the gas is compressed in the meantime.

  Here, when the gas to be compressed is a gas that has a low molecular weight and is difficult to compress, for example, hydrogen, it is necessary to increase the number of impeller stages in order to compress the gas to a high compression rate as with a normal gas. . However, when the number of impeller stages is increased, the number of casings for accommodating the impellers is increased, which increases the size of the entire centrifugal compressor and increases the cost due to an increase in material costs.

  In addition, when the number of casings increases, the number of bearings provided in the casing and rotatably supporting the rotating shaft also increases. If it does so, while the bearing loss of a rotating shaft will increase, the maintenance of a bearing will also become complicated. For this reason, it is preferable to minimize the number of casings by minimizing the number of impeller stages.

  Therefore, as a means for compressing a gas that is difficult to compress, such as hydrogen, to a high compression ratio without increasing the number of stages of the impeller, the rotational speed of the impeller in the circumferential direction (hereinafter referred to as “peripheral speed”) is increased. A method is mentioned. According to this method, since the number of casings does not increase, the entire centrifugal compressor does not increase in size and the material cost does not increase.

  However, the conventional impeller has a problem in that when the peripheral speed of the impeller is increased, the centrifugal force increases abruptly, so that the stress generated in the blade increases. This is because the centrifugal force acting on the blade increases in proportion to the square of the peripheral speed as the peripheral speed of the impeller increases.

  FIG. 8 is a schematic cross-sectional view showing an impeller 70 according to a conventional example fixed to the rotation shaft S. As described above, a so-called open impeller (see, for example, Patent Document 1) in which the distal end portion of the blade 72 whose base end portion is fixed to the disk 71 is not covered by a shroud (not shown) is used. Since it is not structurally reinforced, when the peripheral speed of the impeller 70 increases and the centrifugal force increases, the blade 72 that receives the centrifugal force is relatively easily deformed or damaged. Therefore, a method of increasing the thickness of the blade 72 is conventionally used as means for suppressing the stress of the blade 72 caused by centrifugal force.

  However, if the thickness of the blade 72 is increased to alleviate the stress due to the centrifugal force, the weight of the blade 72 increases, so that the bending stress acting on the disk 71 increases. Therefore, as shown in FIG. 8, the radially outer portion (the portion indicated by the two-dot chain line in FIG. 8) where the axial thickness of the disk 71 is thin is likely to be deformed or damaged by bending stress. . As a means for preventing such deformation and damage of the disk 71 due to bending stress, there is a method of increasing the thickness of the disk 71 (see, for example, Patent Document 2).

JP 07-49099 A JP 2001-304181 A

  However, with the conventional impeller 70, increasing the thickness of the disk 71 to prevent damage to the disk 71 due to bending stress has the advantage of increasing the strength of the disk 71 against bending stress, but increases the weight of the disk 71. As a result, the centrifugal force increases, and the axial length of the rotor composed of the rotating shaft S, the impeller 70, and the like becomes longer, and the stability of the rotor is deteriorated.

  The present invention has been made in consideration of such circumstances, and its purpose is to adversely affect both the centrifugal force and the stability of the rotor when the thickness of the blade is increased to ensure the strength against the centrifugal force. It is an object of the present invention to provide a means for reducing bending stress acting on the radially outer portion of the disk without exerting any influence on the disk.

In order to achieve the above object, the present invention employs the following means. That is, the impeller according to the present invention, a disk-shaped disk which is rotatably mounted integrally with the rotary shaft, the surface more provided to protrude circumferentially from the disc, at least in the radially outer portion, said rotary shaft And a blade provided with a cavity for suppressing the weight by forming a substantially circular cross section perpendicular to the axial direction of the disk. The blade penetrates the disk and communicates the cavity and the back side of the disk. In addition, a vent hole having a smaller diameter than that of the hollow portion is provided.

According to such a configuration, since the weight of the blade is suppressed by providing a hollow portion at least in the radially outer portion of the blade, even if the peripheral speed of the impeller becomes high, the centrifugal force is not increased and the rotor is increased. The bending stress acting on the radially outer portion of the disk can be reduced without deteriorating the stability of the disk.
Also, according to such a configuration, the cavity formed inside the blade communicates with the back side of the disk through the vent hole, so that when the pressure changes outside the cavity, the cavity The pressure also changes inside. Therefore, no stress acts on the blade due to the pressure difference between the inside and the outside of the cavity. Further, the vent hole is provided through the disk, and one end opening of the vent hole is not formed on the surface of the blade. Therefore, the gas flow guided by the blade is not adversely affected by the one end opening of the vent hole.

Further, in the impeller according to the present invention, the blade has a range in which a thickness in a direction substantially perpendicular to a radial direction at a base end portion connected to the disk is larger than a thickness of the disk, The range in which the cavity is provided in the blade is such that the thickness in the direction substantially perpendicular to the radial direction at the base end connected to the disk is larger than the thickness of the disk along the radial direction. It is characterized by being.

  According to such a configuration, the cavity is formed in the radial outer portion where the thickness of the base end portion of the blade in the direction substantially perpendicular to the radial direction is larger than the thickness of the disc, that is, the thickness of the disc becomes relatively thin. Therefore, it is possible to more reliably prevent the disk from being damaged by the bending stress.

  The impeller according to the present invention is characterized in that the hollow portion is filled with a material having a lower density than the material forming the blade.

  According to such a configuration, since a predetermined material is filled in the cavity, it is possible to prevent the generation of a so-called secondary flow that adversely affects the gas flow inside or around the cavity. Can do. Further, since the material filled in the hollow portion has a lower density than the material forming the blade, the role of the hollow portion for suppressing the weight of the blade is not hindered.

  According to the impeller of the present invention, when the thickness of the blade is increased to ensure the strength against centrifugal force, it acts on the radially outer portion of the disk without adversely affecting both the centrifugal force and the stability of the rotor. Bending stress can be reduced.

It is a schematic sectional drawing which shows the centrifugal compressor provided with the impeller which concerns on the reference example of this invention. It is a schematic plan view which shows the state which looked at the impeller which concerns on the reference example of this invention from the back surface side. It is a figure which shows the modification of the impeller which concerns on the reference example of this invention, Comprising: It is a schematic plan view which shows the state seen from the back surface side. It is a schematic perspective view which shows the state which looked at one blade of the impeller which concerns on the reference example of this invention from the base end part side. It is a schematic sectional drawing which shows the BB cross section in FIG. 4 about the impeller of a reference example. It is a schematic sectional drawing which shows the BB cross section in FIG. 4 about the impeller of 1st Embodiment. It is a schematic sectional drawing which shows the BB cross section in FIG. 4 about the impeller of 2nd Embodiment. It is a schematic sectional drawing which shows the impeller which concerns on a prior art example.

[Reference example]
Embodiments of the present invention will be described below with reference to the drawings. First, the configuration of an impeller according to a reference example of the present invention will be described. FIG. 1 is a schematic cross-sectional view showing a centrifugal compressor 1 including an impeller 10 according to a reference example of the present invention. The centrifugal compressor 1 includes a casing 2 as a housing, a rotating shaft 3 provided through the central portion of the casing 2, and a plurality of impellers 10 provided along the rotating shaft 3. Is.

  The casing 2 is for housing the impeller 10 and the rotating shaft 3. As shown in FIG. 1, the casing 2 includes a casing body 21 having a substantially cylindrical shape, a pair of journal bearings 22 provided at both ends in the longitudinal direction of the casing body 21, and the longitudinal direction of the casing body 21. And a thrust bearing 23 provided at one end thereof.

  As shown in FIG. 1, the casing body 21 has a substantially columnar shape, and a shaft insertion hole 211 is formed through the central portion thereof. In addition, a suction port 212 through which a gas to be compressed flows from the outside to the inside is opened at one end side in the longitudinal direction of the casing body 21, while a compressed gas is fed from the inside to the other end side in the longitudinal direction. A discharge port 213 that flows out to the outside is provided. In the casing 2, an internal space 214 is provided which communicates with the suction port 212 and the discharge port 213, and repeats the diameter reduction and the diameter expansion in the longitudinal direction.

  The journal bearing 22 and the thrust bearing 23 are for supporting the rotary shaft 3 so as to be rotatable about the axis. As shown in FIG. 1, one side of the journal bearing 22 is fitted into a shaft insertion hole 211 on one end side of the casing body 21, and the other is attached to the other end side of the casing body 21. It is housed inside the bearing case 24. Further, the thrust bearing 23 is accommodated in a bearing case 25 attached to one end side of the casing body 21.

  The rotating shaft 3 is rotationally driven by a driving machine (not shown) (turbine, motor, etc.). As shown in FIG. 1, the rotating shaft 3 is inserted through a shaft insertion hole 211 of the casing body 21, and both end portions in the longitudinal direction protrude to the outside of the casing body 21. The rotating shaft 3 is rotatably supported by inserting both ends of the rotating shaft 3 in the journal bearing 22 and the thrust bearing 23, respectively.

  The impeller 10 compresses gas using centrifugal force. As shown in FIG. 1, the impeller 10 includes a disk-shaped disk 101 that is coaxially attached to the rotary shaft 3, a plurality of blades 102 that protrude from the surface of the disk 101, And a cavity 103 drilled so as to reach the blade 102 from the back surface. The impeller 10 configured as described above is housed inside the casing 2, and the rotary shaft 3 is inserted into and fixed to a shaft insertion hole 101 a formed through the disk 101. Thereby, the impeller 10 rotates integrally with the rotating shaft 3 as the rotating shaft 3 rotates. A gap between a plurality of blades 102 constituting the impeller 10 or a gap between the blade 102 and the casing body 21 is configured as a flow path 104 through which gas flows. In this reference example, six impellers 10 are provided at predetermined intervals along the axial direction of the rotary shaft 3, but the number of impellers 10 is not limited to this, and the design can be changed as appropriate. One is OK.

  Here, FIG. 2 is a view of the impeller 10 seen from the back side of the disk 101, that is, a view seen from the side opposite to the protruding side of the blade 102. FIG. As shown in FIGS. 1 and 2, the disk 101 constituting the impeller 10 is formed in a substantially circular shape when viewed in the axial direction, and a hub portion 101 b protruding in one axial direction is provided at the center thereof. And the surface of the one axial side is curvedly formed so that it may go to an axial direction from a radial direction as it goes to an inner peripheral side from an outer peripheral side. The other surface is formed in a plane substantially orthogonal to the rotation shaft 3. For this reason, the thickness of the disk 101 is the thinnest on the outer peripheral side and becomes thicker toward the inner peripheral side. Further, a shaft insertion hole 101a through which the rotation shaft 3 is inserted is formed through the hub portion 101b. The shape of the disk 101 is not limited to this reference example, and can be changed in design as appropriate.

  On the other hand, as shown in FIG. 2, a plurality of blades 102 constituting the impeller 10 are provided on the surface of the disk 101 at a predetermined interval in the circumferential direction. Here, FIG. 4 is a schematic perspective view showing a state in which one of the blades 102 is viewed from the base end side, that is, the connection side to the disk 101. In FIG. 4, the disk 101 positioned on the front side of the blade 102 is indicated by a broken line. The blade 102 is for guiding the gas to be compressed in a predetermined flow direction. The blade 102 has a curved shape along the surface of the disk 101 in a side view as shown in FIG. 1, and is curved so as to extend radially from the center of the disk 101 in a plan view as shown in FIG. It has a shape. Further, as shown in FIG. 4, the blade 102 has a base end portion with a thickness d1 that gradually increases from the radially inner side of the disk 101 toward the radially outer side. 5 is a schematic cross-sectional view showing a BB cross section in FIG. The blade 102 has a substantially triangular cross section as its thickness gradually decreases from the proximal end portion toward the distal end portion. The shape of the blade 102 can be appropriately changed in accordance with the shape of the disk 101.

  The cavity 103 is for suppressing the weight of the blade 102. As shown in FIG. 5, the cavity 103 is formed so as to penetrate the disk 101 from the back surface of the disk 101, reach a predetermined depth of the blade 102, and not penetrate the blade 102. As shown in FIGS. 2 and 4, the hollow portion 103 has a substantially circular cross section, and a plurality of hollow portions 103 are formed in the radially outer portions of the disk 101 and the blade 102. Here, as shown in FIG. 4, the radially outer portion has a thickness d1 in a direction substantially perpendicular to the radial direction at the base end portion of the blade 102 that gradually increases from the radially inner side toward the radially outer side. As shown in FIG. 5, this means a range that increases beyond the thickness d2 of the disk 101.

  In addition, the drilling position, the number, the cross-sectional shape, and the like of the hollow portion 103 are not limited to this reference example, and can be appropriately changed in design. For example, the cross-sectional shape of the cavity 103 may be an elongated hole shape extending in the radial direction of the disk 101 as shown in FIG. 3 instead of the substantially circular cross-section of this reference example, and details are not shown in the figure. It may be a substantially polygonal shape or a substantially elliptical shape. Further, the position where the cavity 103 is provided in the disk 101 and the blade 102 may be provided not only in the radially outer portion but also in the radially central portion and the radially inner portion.

  In this reference example, as a procedure for forming the cavity 103, the disk 101 and the blade 102 are connected by welding, brazing, or the like, and then drilled from the back side of the disk 101. However, before connecting the disk 101 and the blade 102, the cavity 103 may be formed in the disk 101 and the blade 102 in a separated state, and then the disk 101 and the blade 102 may be connected. In this case, the cavity 103 formed through the disk 101 can be drilled from the surface side of the disk 101. Further, the design of the disk 101, the blade 102, and the cavity 103 can be changed as appropriate, for example, by integrally forming by forging or casting.

  Next, the effect of the impeller 10 according to the reference example will be described. The impeller 10 according to the present reference example is installed in the centrifugal compressor 1 that compresses, for example, hydrogen gas having a small molecular weight that is difficult to compress. In such a centrifugal compressor 1, as described above, the peripheral speed of the impeller 10 is increased to achieve a high compression ratio, and the blade 102 is prevented from being deformed or damaged by the increased centrifugal force. The thickness is increased. However, when the blade 102 is formed thick, the weight of the blade 102 increases, so that the bending stress acting on the disk 101 to which the blade 102 is fixed increases. As a result, there is a problem that the disk 101 is easily deformed or damaged by bending stress at the radially outer portion where the disk 101 is formed thin.

  However, in the impeller 10 according to the reference example, as described above, the cavity 103 is provided in the radially outer portion of the blade 102, and the weight of the blade 102 is suppressed in the radially outer portion. Accordingly, the bending stress acting on the disk 101 in the radially outer portion is reduced, so that deformation and damage of the disk 101 due to the bending stress can be prevented. Moreover, when the cavity 103 is formed in the radially outer portion, the weight of the disk 101 and the blade 102 is suppressed, so that the centrifugal force acting on the disk 101 and the blade 102 is reduced, and the rotating shaft 3 and the impeller 10 are reduced. The stability of the rotor composed of the above and the like is not deteriorated by the presence of the cavity 103.

  In addition, by providing the cavity 103 inside and securing the thickness of the member outside, it is possible to secure the secondary moment of section necessary for the blade 102. For this reason, rigidity can be ensured while reducing the weight of the blade 102 by the cavity 103 without sacrificing the aerodynamic characteristics.

  Further, in this reference example, the centrifugal compressor 1 that compresses hydrogen gas has been described as an example. However, for example, a gas having a low molecular weight such as helium gas or natural gas may be compressed by the centrifugal compressor 1. The impeller 10 can be applied to the centrifugal compressor 1 having a high peripheral speed regardless of the type of gas to be compressed. Furthermore, the impeller 10 can be applied not only to the centrifugal compressor 1 but also to a radial flow type rotary machine including a gas turbine, an expander, a turbocharger, etc. (not shown).

[First Embodiment]
Next, the configuration of the impeller 10 according to the first embodiment will be described. The centrifugal compressor 1 including the impeller 10 according to the first embodiment is different from the centrifugal compressor 1 of the reference example shown in FIG. 1 only in the configuration of the impeller 10. Since other configurations are the same as those of the reference example, the same reference numerals as those of the reference example are used, and description thereof is omitted here.

  As shown in FIG. 1, the impeller 10 of the present embodiment also includes a disk-shaped disk 101 and a plurality of blades 102 provided so as to protrude from the surface of the disk 101. Here, the blade 102 of the present embodiment has the same configuration as the blade 102 of the reference example shown in FIG. 4, and a cavity 103 is formed in the radially outer portion thereof.

  Here, FIG. 6 is a diagram showing a cross section taken along the line BB in FIG. 4 for the impeller 10 of the present embodiment. In the disk 101 of this embodiment, the cavity 103 as in the reference example is not formed, and a vent hole 101d having a smaller diameter than the cavity 103 is formed through the disk 101. The cavity 103 and the back side of the disk 101 And communicate with. According to such a configuration, when the pressure changes outside the impeller 10, the pressure also changes inside the cavity 103 through the vent hole 101d. Therefore, no stress acts on the blade 102 due to the pressure difference between the inside and the outside of the cavity 103. Further, the vent hole 101 d is provided through the disk 101, and one end opening is formed on the surface of the disk 101. Therefore, compared with the case where the vent hole 101d is formed through the blade 102 and its one end opening is formed on the surface of the blade 102, the one end opening of the vent hole 101d has an adverse effect on the gas flow flowing along the blade 102. It is difficult to give.

[Second Embodiment]
Next, the configuration of the impeller 10 according to the second embodiment will be described. The centrifugal compressor 1 provided with the impeller 10 according to the second embodiment is different from the centrifugal compressor 1 of the reference example shown in FIG. 1 only in the configuration of the impeller 10. Since other configurations are the same as those of the reference example, the same reference numerals as those of the reference example are used, and description thereof is omitted here.

As shown in FIG. 1, the impeller 10 of the present embodiment also includes a disk-shaped disk 101 and a plurality of blades 102 provided so as to protrude from the surface of the disk 101. Here, the disc 101 of the present embodiment has the same configuration as the disc 101 of the reference example shown in FIG. 2, and a plurality of cavities 103 are formed through the radially outer portion thereof.
On the other hand, the blade 102 of this embodiment also has the same configuration as the blade 102 of the reference example shown in FIG. 4, and the cavity 103 is formed so as to communicate with the cavity 103 of the disk 101.

  Here, FIG. 7 is a diagram showing a cross section taken along the line BB in FIG. 4 for the impeller 10 of the present embodiment. In this embodiment, the cavity 103 formed in the blade 102 and the disk 101 is filled with a resin 30 having a lower density than the material forming the blade 102 so as to close the opening on the back surface side of the disk 101 of the cavity 103. A lid member 31 for preventing leakage of the resin 30 is provided. However, if there is no risk of the resin 30 being completely solidified or leaking, the lid member 31 may not be provided.

  According to such a configuration, since the resin 30 filled in the cavity 103 has a lower density than the material forming the blade 102, the weight of the blade 102 is suppressed in the radially outer portion, and the same effect as in the reference example is achieved. Is obtained. In addition, since the hollow portion 103 is filled with the resin 30, it is possible to prevent the generation of a so-called secondary flow that adversely affects the gas flow when the gas flowing through the flow path 104 flows into the hollow portion 103. it can. Furthermore, since the cavity 30 is filled with the resin 30, it is possible to suppress an increase in windage loss in the space on the back side when the disk 101 is rotated.

  The material for filling the cavity 103 is not limited to the resin 30 as long as it has a lower density than the material forming the blade 102, and other members may be used. Further, in this embodiment, as shown in FIG. 7, the resin 30 is filled not only in the cavity 103 formed in the blade 102 but also in the cavity 103 formed in the disk 101, but at least formed in the blade 102. It is sufficient to fill the hollow portion 103 with the resin 30, and the hollow portion 103 formed in the disk 101 is not necessarily filled with the resin 30. Moreover, it replaces with this embodiment and the same effect is acquired also by filling the cavity 30 of the impeller 10 of 1st Embodiment with the resin 30. FIG.

  The various shapes, combinations, operation procedures, and the like of the constituent members shown in the reference examples and embodiments described above are merely examples, and can be variously changed based on design requirements and the like without departing from the gist of the present invention. .

DESCRIPTION OF SYMBOLS 1 Centrifugal compressor 10 Impeller 101 Disc 101a Shaft insertion hole 101b Hub part 101d Vent hole 102 Blade 103 Cavity part 104 Channel 2 Casing 21 Casing main body 211 Shaft insertion hole 212 Inlet 213 Outlet 214 Inner space 22 Journal bearing 23 Thrust bearing 24 Bearing case 25 Bearing case 3 Rotating shaft 30 Resin 31 Lid member 70 Impeller 71 Disc 72 Blade S Rotating shaft

Claims (3)

A disc-like disc that is rotatably attached to the rotary shaft;
A blade that protrudes from the surface of the disk and is provided in the circumferential direction, and at least a radially outer portion is provided with a hollow portion for suppressing weight by forming a substantially circular cross section perpendicular to the axial direction of the rotating shaft. When,
With
An impeller that penetrates the disk, communicates the cavity and the back side of the disk, and is provided with a vent hole having a smaller diameter than the cavity. The blade has a range in which the thickness in the direction substantially perpendicular to the radial direction at the base end connected to the disk exceeds the thickness of the disk;
The range in which the hollow portion is provided in the blade is such that the thickness in the direction substantially perpendicular to the radial direction at the base end portion is larger than the thickness of the disc along the radial direction. The impeller according to claim 1.   The impeller according to claim 1 or 2, wherein the hollow portion is filled with a material having a lower density than a material forming the blade.

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