JP2003042099A - Turbo fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turbo fluid machine controlling noise generated due to interference of grooves on a casing inner circumference surface for stabling head-discharge characteristics and impeller blades. SOLUTION: A plurality of grooves 4 are formed on the inner circumference surface of the roughly cylindrical casing 2 from an inlet side of the blades to an existing area of the blades in a pressure gradient direction of operation fluid to eliminate an increasing tendency of the head-discharge characteristics. The casing 2 is provided with a casing liner 5 and a communication hole 8 together with the plurality of grooves is formed on an inner circumference surface of the casing liner. Consequently, a resonance type silencer (header tank chamber 9) connected to a position close to a position where the grooves 4 and the blades of the impeller 1 oppose is constructed. A dominant frequency of the resonance type silencer is set corresponding to noise caused by interference between the grooves and the blades by suitably setting volume thereof to surely reduce the noise.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbo type fluid machine in which a liquid such as water is used as a working fluid, and in particular, swirl and vane stall due to a recirculation flow at a blade inlet regardless of type and fluid. The present invention relates to a turbo type fluid machine capable of preventing flow instability by suppressing the flow instability.

[0002]

2. Description of the Related Art FIG. 11 is a typical head-flow characteristic of a turbo type fluid machine including a conventional mixed flow pump, where the horizontal axis is a parameter representing a flow rate and the vertical axis is a parameter representing a head. That is, in the low flow rate range, the head decreases as the flow rate increases, but while the flow rate is in the S region, the head also increases as the flow rate increases (rightward rising characteristic). Then, when the flow rate increases above the rightward rising characteristic region, the head decreases again as the flow rate increases. And
When the turbomachine is operated at a flow rate in the above-mentioned upward rising characteristic region, so-called surging occurs, which is a phenomenon in which a lump of fluid self-oscillates in a pipe line.

With such a right-up characteristic, a recirculation flow is generated at the outer edge of the impeller inlet when the flow rate of the fluid flowing through the turbomachine becomes low, and at this time, the flow path of the fluid entering the impeller blade 1 is narrowed. This is caused by swirling of the fluid.

In order to improve the rightward rising characteristic, for example, Japanese Patent Laid-Open Nos. 2000-303995 and 2001-8.
As shown in No. 2392, etc., a plurality of pumps are provided in the casing pressure of the mixed flow pump constituting the turbomachine in the direction of the pump pressure gradient (axial direction) at the position facing the tips of the blades of the impeller provided inside. A structure for forming a book groove has been proposed.

[0005]

However, in the above-mentioned conventional turbomachine, when the above-mentioned groove in the axial direction of the pump is formed on the inner surface of the casing, it is possible to prevent the fluid from swirling. It will be possible,
On the other hand, the following problems occur. That is, especially when the NPSH of the pump is low, a phenomenon in which vibration and noise of the pump abnormally increase is often found. The following are possible causes of this phenomenon.

That is, interference occurs between the blade of the impeller blade rotating in the casing and the groove 4 of the stationary casing (which is also considered to be a kind of stationary blade), and this blade Due to interference between the blades, pressure fluctuations occur when the moving blades of the impeller blades pass over the grooves. Further, in particular, when the suction pressure of the pump or the like is low, the fluid pressure inside the pump may be equal to or lower than the saturated vapor pressure, and cavitation may occur in the fluid. This generated cavitation collapses near the entrance of the impeller, but at that time, along with the collapse of this cavitation,
It is thought that abnormal vibrations and noise will be introduced.

Therefore, the present invention has been made in view of the above-mentioned problems in the prior art, that is, the plurality of grooves are formed on the inner surface of the casing, which is also seen in the above-mentioned prior art, and it also causes the above-mentioned surging. The rise-right characteristic is eliminated, and the lift-flow rate characteristic without the rise-right characteristic is achieved, and at the same time, the increase in noise caused by the interference between the groove formed on the inner surface of the casing and the impeller blade, which is seen in the above-mentioned prior art, is suppressed. As a result, in addition to being excellent in performance,
An object of the present invention is to provide a turbo type fluid machine that generates less noise.

[0008]

The present invention has been achieved based on the findings of the inventors regarding the causes of the above-mentioned abnormal vibrations and noises. To achieve the above object, first, According to the present invention, there is provided a turbo type fluid machine in which an impeller is rotatably mounted inside a substantially cylindrical casing, wherein an inner peripheral surface of the casing is provided with a blade inlet side of the impeller. In a structure in which a plurality of grooves are formed in the pressure gradient direction of the working fluid over the existing region of the blades on the inner peripheral surface of the casing, a plurality of grooves on the inner peripheral surface of the casing are provided in a part of the casing. There is provided a turbo type fluid machine having a silencer connected to the vicinity of a position where the blades of the impeller face each other.

Further, according to the present invention, in the above turbo type fluid machine, the silencer is a resonance silencer, and further, the resonance silencer constituting the silencer is excellent in its superiority. It is preferable that the frequency to be set is set based on noise caused by interference between the plurality of grooves on the inner peripheral surface of the casing and the blades of the impeller.

In addition, according to the present invention, in the above turbo type fluid machine, the casing includes a casing liner in which the plurality of grooves are formed on an inner peripheral surface thereof and a communication hole is formed in a part thereof. And, the casing liner is attached to the inner peripheral side of the casing,
It is preferable to form the resonance silencer between the inner peripheral side of the casing and the outer peripheral side of the casing liner. Furthermore, the communication hole is a bottom surface of the plurality of grooves formed on the inner peripheral surface of the casing liner, and is provided on the downstream side of the blade leading edge position of the impeller, and, in particular,
It is preferable that the volume of the resonance silencer, the number of the communication holes, the diameter, and the length of the resonance silencer are set so as to satisfy the following formula.

[Equation 2]

According to this, the resonance frequency of the resonance type silencer is set so as to coincide with the dominant frequency of pressure fluctuation caused by the interference between the impeller and the groove, so that the silencing effect is remarkable at the desired frequency. It is possible to construct a resonance silencer.

Further, according to the present invention, in the turbo fluid machine described above, a resonance type silencer is formed by forming a through hole communicating with the outside on the outer peripheral side of the casing forming the resonance type silencer. It is possible to discharge the air that accumulates inside and the sediment that accumulates to the outside.
At the outlet of the through hole, it is preferable to provide a valve that is a means for opening and closing the through hole.

Further, in the present invention, in the above turbo type fluid machine, for example, inside the resonance type silencer,
A damping material such as glass wool or a sponge containing innumerable closed cells, which is filled with a sound absorbing material, or an elastic material is installed in a portion where the casing liner is attached to the casing, that is, it has higher elasticity than metal. For example, by inserting a liner or packing made of hard rubber, or by forming the casing liner and the casing, for example, by applying a metal material having a vibration damping function, such as damping steel or casting, It becomes possible to provide a turbo fluid machine that is excellent in silencing and reducing noise.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the embodiments of the present invention will be described below with reference to the accompanying drawings. First, FIG. 2 shows an overall configuration of a turbo type fluid machine according to a first embodiment of the present invention in cross section. In this figure, an impeller having a plurality of blades in the radial direction and indicated by reference numeral 1 in the figure is rotatably arranged inside a substantially cylindrical casing 2. Further, a pump shaft 3 extending in the axial direction of the impeller 1 is connected to the impeller 1 at a substantially central portion of the casing 2.
Although not shown, the impeller 1 is rotationally driven by a rotating means such as an electric motor to rotate in the casing 2, thereby moving the fluid in a direction indicated by an arrow in the figure.

Further, the generation of the recirculation flow indicated by the double arrow circle in the above figure is prevented to eliminate the S region (rightward rising characteristic) in the head-flow rate characteristic of the turbo type fluid machine, and thus surging is performed. In order to avoid the occurrence of the above, a plurality of grooves are formed on the inner peripheral surface of the casing 2 so as to connect the insides of the blades (moving blades) of the impeller 1 in the fluid pressure gradient direction. In addition, the groove forming portion on the inner peripheral surface of the casing 2 is shown by a dashed line in the drawing,
An enlarged cross-sectional view of the part is shown in the attached FIG.

As is apparent from FIG. 3, the grooves 4 formed in the axial direction of the casing 2 on the inner peripheral surface of the casing 2 of the turbomachine have blades (moving blades) of the impeller 1.
At a position opposite to the tip (front edge) of the blade and from the inlet side of the working fluid in the blade of the impeller 1 (in FIG. 3, the left side of the leading edge of the blade of the impeller 1) to the existence area of the blade on the inner surface of the casing. Formed across is similar to the conventional turbo fluid machine described above. Further, the symbol C _t in the drawing indicates a gap between the impeller 1 and the inner peripheral surface of the casing 2.

Further, in the structure of the pump which is the turbomachine having the above-mentioned structure, in the present invention, the casing 2 is used to form the resonance type silencer, and the cavitation generated in the fluid flowing inside. The abnormal vibration and noise accompanying the collapse near the entrance of the impeller 1 are reduced.

This will be described more specifically with reference to the attached FIG. 1 (a). In the pump, which is a turbomachine described below, the casing 2 has a bell mouth 6 and a casing liner 5 that form a pump suction port.
The bell mouth 6 and the casing liner 5, together with the rotating impeller 1 and the guide vanes 7, constitute a flow path for a fluid such as water flowing inside. Also in this figure, the impeller 1 and the casing liner 5 are also shown.
There is a gap between them, which is also indicated by the symbol C _t . In addition, in the figure, a portion indicated by a broken line circle is enlarged and shown in FIG.

The casing liner 5 attached to the casing 2 forms a header tank chamber 9 between the outer peripheral surface of the casing liner 5 and the inner peripheral surface of the casing 2. As is clear from the drawing, the plurality of grooves 4 described above are formed on the inner peripheral surface of the casing liner 5 attached to the casing 2.
A communication hole 8 penetrating the casing liner 5 is formed in a part of the bottom surface of the. The communication hole 8 is formed at a position indicated by a symbol L in the drawing, slightly downstream from the front edge of the blade 1 in the axial direction of the casing 2.

Here, as described above, the header tank chamber 9 formed by the outer peripheral surface of the casing liner 5 and the inner peripheral surface of the casing 2 constitutes a so-called Helmholtz resonance silencer. The volume V of the tank 9 and the shape parameter of the communication hole 4 are formed so that the relationship represented by the following equation is established.

[Equation 3]

The above-mentioned (formula 1) is a formula for obtaining the resonance frequency of the resonance-type silencer.
Japan Acoustic Materials Association: Noise and Vibration Countermeasure Handbook ",
Gihodo Publishing, July 1993, p. 291. Etc.

Here, the resonance frequency is caused by the vibration generated by the interference (interference between moving and stationary blades) between the groove 4 which is the stationary portion and the blade of the impeller 1 which is the moving blade in the above-mentioned structure. It is the dominant frequency of noise. For example, groove depth: 12
mm, groove width: 2.4 mm The above groove 4 is inserted into the casing liner 5.
The number of grooves n: 25 is formed equidistantly on the entire inner circumference of the above, and this is combined with the impeller 1 rotating at the number of blades Z: 4 and the rotation speed N: 1300 rpm (21.67 Hz). FIG. 4 attached herewith shows an example of the result of measuring the noise generated inside the pump outside the pump and performing a frequency analysis on the measured noise. Here, in the above (Formula 1), N: impeller rotation speed = 21.67 Hz, n: number of grooves = 25, Z: number of impeller blades = 4. Therefore, in the case of FIG. 4, one peak exists in the vicinity of f = 12Nn = 1040 Hz, and the noise of this frequency is characterized by being annoying to the human ear.

Therefore, according to the present invention, this noise f =
The volume of the header tank 9 and the shape (length, radius, number) of the communication holes 8 are appropriately designed so that the frequency of 1040 Hz becomes the resonance frequency.

In the pump constructed as described above,
The pressure fluctuation generated by the interference between the blade of the impeller 1 and the groove 4 is transmitted through the communication hole 8 formed in the bottom surface of the groove 4,
Enter the resonance chamber in the header tank 9. The resonance frequency fr in the resonance chamber of the header tank 9 is, as described above,
The energy of the fluctuating pressure is consumed in the resonance chamber because it is preset so as to match the excellent frequency component of noise (vibration) which is pressure fluctuation. That is, the pressure fluctuation generated by the interference between the blade of the impeller 1 and the groove 4 is attenuated, and the noise is surely reduced accordingly.

Further, as apparent from the above description,
These grooves 4 forming the Helmholtz resonant silencer
A plurality of communicating holes 8 are arranged in the inner circumferential direction of the casing liner 5 attached to the casing 2 so as to face the blade tip (front edge) of the impeller 1. Therefore, the pressure fluctuations due to the interference between the grooves 4 and the blades of the impeller 1 have different phases in each part (each communication hole 8). However, the pressure fluctuations (noise) having the different phases eventually result in It will be synthesized in the header tank 9,
Furthermore, the effect of reducing the amplitude of the pressure fluctuation (noise) in the header tank 9 is also added, and the noise that is the vibration due to the pressure fluctuation is significantly reduced.

In order to form the Helmholtz resonance type silencer, a communication hole 8 formed in the bottom surface of these grooves 4 is formed.
The effect of noise reduction by is as described above. On the other hand, a communication hole 8 is formed on the bottom surface of these grooves 4 and penetrates the header tank chamber 9 which is the resonance type silencer,
However, the hole diameter of these communication holes 8 is smaller than the groove width of the groove 4, and therefore the flow of the fluid flowing in and out through these communication holes 8 is basically not formed. Therefore, the effect of improving the stability of the pump head curve by the plurality of grooves 4 formed on the inner circumference of the casing liner 5 of the casing 2 is the same as the conventional one. That is, in addition to the noise reduction effect of the resonance silencer, the same effect of stabilizing the lift curve as in the conventional case can be obtained.

Next, referring to the attached FIG. 5, there is shown a pump which is a turbomachine according to a second embodiment of the present invention.
Note that, also in this embodiment, the same reference numerals as those in FIG. 1 denote the same constituent elements, and
In order to avoid duplication of explanation, the explanation will be added focusing on the difference.

In the second embodiment, as is apparent from FIG. 5, the header tank chamber 9 is provided between the outer peripheral surface of the casing liner 5 attached to the casing 2 and the inner peripheral surface of the casing 2. In addition to providing the resonance chamber, the casing 2 is further provided with through holes 10 and 12 in order to electrically connect both ends of the header tank 9 to the outside.

According to this structure, during operation of the pump,
Even if air or sediment that enters the resonance chamber that forms the header tank 9 enters, the air or sediment that is inside the resonance chamber can be discharged to the outside through these holes 10 and 12. Therefore, the resonance chamber can be constantly filled with water as a working fluid, and the function as the resonance chamber can be continuously maintained.

Next, FIG. 6 shows a third embodiment of the present invention. Note that, also in this embodiment,
Further, the same reference numerals as the reference numerals in FIG. 5 indicate the same constituent elements, and in the following, in order to avoid duplication of description, the difference will be mainly described.

As is apparent from the drawing, the pump according to the third embodiment has the through holes 9 and 10 formed in the casing 2 in the embodiment shown in FIG. The valves 12 and 13 are installed. It should be noted that these valves 12 and 13 are opened, for example, during maintenance work after the pump has been operated for a predetermined period of time, and are closed during normal operation.

According to the pump of the third embodiment having such a configuration, even if air remains in the header tank 9 forming the resonance chamber and sediment enters and precipitates, the valves 12, 1
By opening 3, the residual air and the sediment that have settled can be discharged to the outside, and these valves are closed after the discharging operation. According to this, during the operation of the pump, the header tank 9 forming the resonance chamber only communicates with the working fluid through the above-mentioned communication hole 8 and communicates with the outside through the through holes 9 and 10. Therefore, the action and effect of the header tank 9 as a resonance chamber can be enhanced.

Further, FIG. 7 attached herewith shows a fourth embodiment of the present invention. As is clear from the drawing, in the fourth embodiment, in the pump which is the turbomachine according to the first embodiment, the outer peripheral surface of the casing liner 5 attached to the casing 2 and the casing. A resonance chamber consisting of a header tank chamber 9 is provided between the casing liner 5 and the inner peripheral surface of the casing 2, and a hole 14 penetrating from the header tank 9 to the downstream side of the impeller 1 is formed.
It is provided on the wall of. Note that, also in this embodiment, the same reference numerals as those in FIG. 1 denote the same constituent elements.

According to this structure, the water, which is the working fluid having a high pressure at the outlet of the impeller 1 during the operation of the pump, flows into the header tank 9 through the hole 14 and flows upstream (left side in the figure). ), And further flows into each groove 4 through the communication hole 8. As a result, the pressure of the working fluid in the groove 4 is increased, and thus cavitation generated in the groove 4 is suppressed. That is, it is possible to further reduce the generation of noise due to cavitation, and thus it is possible to realize a turbo type fluid machine that generates little noise despite the groove formed on the inner surface of the casing.

Next, FIG. 8 shows a fifth embodiment of the present invention. As is apparent from the figure, in the fifth embodiment, in the structure of the pump which is the turbomachine according to the first embodiment, the outer peripheral surface of the casing liner 5 attached to the casing 2 and the casing. The header tank chamber 9 formed as a resonance chamber between the inner peripheral surface of 2 and the inner peripheral surface is filled with a sound absorbing material 15, such as glass wool or sponge, having a large number of independent bubbles therein. Note that, also in this embodiment, the same reference numerals as those in FIG. 1 denote the same constituent elements.

According to the pump having the above-mentioned structure, in addition to the attenuation of the noise due to the resonance of the header tank chamber 9 formed above, the attenuation of the noise due to the filled sound absorbing material 15 is added. The effect of attenuating noise due to the header tank chamber formed with is increased. Also,
Simultaneously with the filling of the sound absorbing material 15 such as glass wool or sponge as described above, the material of the casing liner 5 or the casing 2 forming the resonance chamber is also provided with a vibration damping function such as steel or a casting. It is preferable to apply the material because the effect of further reducing noise can be obtained.

Further, FIG. 9 shows a sixth embodiment of the present invention. As is clear from the figure, in the sixth embodiment, when the metal casing liner 5 having the plurality of grooves 4 and the communication holes 8 formed on the inner peripheral surface thereof is attached to the casing 2, A fitting portion with the casing 2,
Further, a liner formed of a material (so-called elastic material), such as rubber, which allows a larger elastic deformation than a metal, for example, in a fitting portion of the flange of the bell mouth 6 and the flange of the guide vane 7 adjacent to this. It is attached with 16 and 17 interposed. Each of the liners 16 and 17 may be composed of two members, or alternatively, may be formed as one ring-shaped component having an L-shaped cross section. Alternatively, a sheet packing liner and a wide ring liner may be fitted. Note that, also in this embodiment, the same reference numerals as those in FIG. 1 denote the same constituent elements.

In this pump structure, when pressure fluctuations act on the groove 4 formed on the inner peripheral surface of the casing liner 5, the casing liner 5 vibrates. However, this casing liner 5 and the above casing 2
Between the bell mouth 6 and the guide vanes 7 and the adjacent liner 1 made of an elastic material.
Because of the interposition of 6 and 17, the vibrations are absorbed by these liners 16 and 17 and are prevented from propagating to other parts. As a result, even if the vibrating component (in this example, the casing liner 5) vibrates, the vibration has a small amplitude due to the absorption by the elastic material of the liners 16 and 17, and the propagation to other components is also suppressed. Therefore, noise will be reduced.

Finally, FIG. 10 attached shows the seventh aspect of the present invention.
An embodiment of is shown. In addition, the seventh embodiment,
In the configuration of the turbomachine pump according to the first embodiment shown in FIG. 1, in particular, the header tank chamber 9 formed as a resonance chamber between the outer peripheral surface of the casing liner 5 and the inner peripheral surface of the casing 2. In this example, the volume V of the casing 2 is larger than that of the above-described embodiment, and as is clear from the figure, the cross-sectional shape of the casing 2 is changed from the "re" shape to the "" shape. Note that, also in this embodiment, the same reference numerals as those in FIG. 1 denote the same constituent elements.

As described in detail above, the resonance frequency of the resonance chamber, which is the header tank chamber 9, is inversely proportional to the square root of the volume V of the resonance chamber, as shown by the above equation (1). That is, in order to set the resonance frequency to a smaller value, it is necessary to increase the volume V of the resonance chamber. In such a case, as shown in the seventh embodiment, the cross-sectional shape of the casing 2 forming the header tank chamber 9 serving as a resonance chamber between the casing liner 5 and the outer peripheral surface thereof is appropriately modified. By doing so, it is possible to set a desired value.

In the above-described various embodiments, the turbofluid machine according to the present invention has been described by taking a pump for pumping water as an example. However, the present invention is not limited to such a pump. Other machines may be used as long as they use a liquid as a working fluid, and since the same effects as described above can be achieved, it is not applicable to them. , It will be clear from the above explanation.

That is, more specifically, the present invention is applicable to a pump having a non-volume type impeller and the liquid to be handled is a pump, or a pump water turbine, and in the normal flow of the recirculation flow at the impeller inlet. It is possible to prevent pre-swirl and vane stall stall to prevent flow instability.
In that case, when cavitation is generated in the impeller and accompanied by an increase in vibration and noise, it can be reduced. That is, the turbo fluid machine according to the present invention is, for example, a turbo fluid machine suitable for a circulating water pump used in a thermal power plant or a mixed flow pump used as a drainage pump for rainwater in a city. be able to.

[0043]

As is apparent from the above detailed description, according to the present invention, a plurality of grooves are formed on the inner surface of the casing to eliminate the rightward rising characteristic that causes the occurrence of surging. At the same time, the increase in noise caused by the interference between the formed groove and the impeller blade is suppressed / reduced at the same time, so that the turbo fluid machine is excellent in performance and generates little noise. In terms of practical use, it is extremely effective.

[Brief description of drawings]

FIG. 1 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller in a mixed flow pump of a turbo type fluid machine according to a first embodiment of the present invention, and a partially enlarged cross-sectional view thereof.

FIG. 2 is a cross-sectional view showing the entire structure of a mixed flow pump that is the turbo fluid machine of the present invention.

FIG. 3 is a view for explaining a groove portion of an impeller and a casing liner in the mixed flow pump which is the turbo type fluid machine,
FIG. 3 is an enlarged cross-sectional view of part A of FIG.

FIG. 4 is a diagram showing an example of a frequency spectrum of noise measured in a pump including a grooved casing to which the present invention is applied.

FIG. 5 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller of a mixed flow pump according to a second embodiment of the present invention.

FIG. 6 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller of a mixed flow pump according to a third embodiment of the present invention.

FIG. 7 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller of a mixed flow pump according to a fourth embodiment of the present invention.

FIG. 8 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller of a mixed flow pump according to a fifth embodiment of the present invention.

FIG. 9 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller of a mixed flow pump according to a sixth embodiment of the present invention.

FIG. 10 is an enlarged cross-sectional view showing a meridional cross-sectional shape near an impeller of a mixed flow pump according to a seventh embodiment of the present invention.

FIG. 11 is a graph showing a typical lift-flow rate characteristic of a turbomachine.

[Explanation of symbols]

1 ... Impeller 2 ... Casing 3 ... Pump shaft 4
... Groove 5 ... Casing liner 6 ... Bell mouth 7 ... Guide vane 8 ... Communication hole 9 ... Header tank chamber (resonance chamber) 1
0, 11 ... Through hole 12, 13 ... Valve 14 ... Through hole 15 ... Sound absorbing material
16, 17 ... Elastic material

Continued front page    (72) Inventor Koichi Irie             603 Jinmachi-cho, Tsuchiura-shi, Ibaraki Japan Co., Ltd.             Tate Manufacturing Industrial Machinery Systems Division F term (reference) 3H034 AA02 AA16 BB03 BB08 BB19                       CC01 CC04 DD05 EE06 EE08

Claims (12)

[Claims] 1. A turbo type fluid machine in which an impeller is rotatably mounted in a substantially cylindrical casing, wherein an inner peripheral surface of the casing is arranged from the inlet side of the impeller blade to the inside of the casing. In a structure in which a plurality of grooves are formed in the pressure gradient direction of the working fluid over the existence region of the blade on the peripheral surface, the plurality of grooves on the inner peripheral surface of the casing and the blade are formed in a part of the casing. A turbo-type fluid machine characterized in that a silencer is formed in the vicinity of a position where the vanes of a vehicle face each other. 2. The turbo type fluid machine according to claim 1, wherein the silencer is a resonance type silencer. 3. The turbo fluid machine according to claim 2, wherein the resonance type silencer forming the silencer has a predominant frequency of a plurality of grooves on the inner peripheral surface of the casing and the impeller. A turbo type fluid machine characterized by being set on the basis of noise caused by interference with blades. 4. The turbo type fluid machine according to claim 2, wherein the casing includes a casing liner in which the plurality of grooves are formed on an inner peripheral surface thereof and a communication hole is formed in a part thereof. The casing liner is attached to the inner peripheral side of the casing, and thus the resonance type silencer is formed between the inner peripheral side of the casing and the outer peripheral side of the casing liner. machine. 5. The turbo fluid machine according to claim 4, wherein the communication hole is a bottom surface of the plurality of grooves formed on an inner peripheral surface of the casing liner, and a blade leading edge position of the impeller. A turbo type fluid machine characterized by being provided further downstream. 6. The turbo fluid machine according to claim 4, wherein the resonance silencer has a volume, a number of the communication holes, and a diameter of the resonance silencer so as to satisfy the following expression. , A turbo type fluid machine characterized in that the length is set. [Equation 1] 7. The turbo type fluid machine according to claim 4, wherein a through hole communicating with the outside is further formed on an outer peripheral side of the casing forming the resonance silencer. Turbo type fluid machine. 8. The turbo type fluid machine according to claim 7, wherein an opening / closing means for the through hole is provided at an outlet of the through hole. 9. The turbo type fluid machine according to claim 4, wherein a part of the casing liner further has a through hole for connecting the resonance silencer to a space near a blade outlet of the impeller. A turbo type fluid machine characterized by having a hole formed therein. 10. The turbo type fluid machine according to claim 4, wherein the resonance type silencer is filled with a sound absorbing material. 11. The turbo type fluid machine according to claim 4, wherein an elastic material is installed in a portion where the casing liner is attached to the casing. 12. The turbo type fluid machine according to claim 4, wherein at least the casing liner and the casing are formed by applying a metal material having a vibration damping function. machine.