JPH11148489A - Water atomizing device for turbo-compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly control the amount of water atomization at all times, and surely reduce a compression work, namely necessary power. SOLUTION: This device is equipped with a water atomizing nozzle provided on the suction side 13 of a turbo-compressor 1, a temperature sensor 10 provided for the discharge side 12 of the turbo-compressor 1, and with a control means 11 controlling the amount of water atomization in such a way that the detected temperature of the temperature sensor reaches the target temperature set to be higher than the saturation temperature of vapor. Since temperature at the discharge side is controlled to be higher than the saturation temperature of vapor, atomized water is entirely voporized, and it is avoided that very small water drops remain because the amount of water atomization is too much. Besides, since temperature at the discharge side 12 is so controlled as to be higher than the target temperature (higher than saturated temperature of vapoe), insufficient cooling due to the too little amount of water atomization can also be avoided. As a result, a compression work, namely necessary power can surely be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a water spray device for a turbo compressor.

[0002]

2. Description of the Related Art Conventionally, there has been known an apparatus in which water is sprayed on a suction side of a turbo compressor, and air which is adiabatically compressed by the heat of vaporization is cooled to approach isothermal compression to reduce compression work. ing.

[0003]

However, if the spray amount of water is too large, all of the water droplets are not vaporized and remain as fine water droplets, so that the impeller gives kinetic energy to the fine water droplets. On the contrary, the compression work becomes large. On the other hand, if the spray amount of water is too small, the cooling effect by the heat of vaporization is small, and the compression work cannot be sufficiently reduced.

SUMMARY OF THE INVENTION An object of the present invention, which has been made in view of the above circumstances, is to provide a water spray device for a turbo compressor which can always appropriately control the spray amount of water and can reduce the compression work, that is, the required power. Is to do.

[0005]

According to a first aspect of the present invention, there is provided a water spray device for a turbo compressor, the water spray nozzle being provided on a suction side of the turbo compressor, and a water spray nozzle provided on a suction side of the turbo compressor. And a control means for controlling the amount of water sprayed by the water spray nozzle so that the temperature detected by the temperature sensor is equal to or higher than the saturation temperature of water vapor. It is.

According to the present invention, the temperature of the discharge side of the turbo-compressor to which water is sprayed is controlled to be equal to or higher than the saturation temperature of steam, so that all of the sprayed water is vaporized. Water droplets are avoided. In addition, since the temperature on the discharge side is controlled to be equal to or higher than the target temperature (saturated temperature of water vapor), insufficient cooling due to an insufficient amount of water spray is also avoided. As a result, the compression work, that is, the required power, is reliably reduced.

Further, the turbo compressor may have a detecting means for detecting whether the turbo compressor is in a load operation or a no-load operation, and a stop means for stopping the water spray of the water spray nozzle during the no-load operation. During the no-load operation, the compression work, that is, the required power is extremely small in the first place, so that the power reduction effect by the water spray is small. Therefore, the water spray is stopped during the no-load operation to simplify the control.

A water spray device for a turbo compressor according to a second aspect of the present invention includes a water spray nozzle provided on the suction side of the turbo compressor, a flow sensor for detecting a flow rate of air passing through the turbo compressor, Determining means for determining the water spray amount of the water spray nozzle based on the air flow rate detected by the flow sensor.

In the present invention, since the temperature (heat amount) on the discharge side, which is a parameter in the first invention, is proportional to the flow rate of the air passing through the turbo compressor, a predetermined ratio of water is sprayed based on the flow rate of the air. Thus, the phenomenon of residual fine water droplets due to overspray and the insufficient cooling phenomenon due to underspray are avoided beforehand.

A water spray device for a turbo compressor according to a third aspect of the present invention is a water spray nozzle provided on a suction side of the turbo compressor, and a power sensor for detecting a required power of a motor for driving the turbo compressor. And a determining means for determining a water spray amount of the water spray nozzle based on the power detected by the power sensor.

According to the present invention, the temperature (heat amount) on the discharge side, which is a parameter in the first invention, is proportional to the required power of the motor for driving the turbo compressor. By spraying, residual phenomena of fine water droplets due to overspraying and insufficient cooling phenomena due to underspraying are avoided beforehand.

The turbo compressor may have a timer for measuring a time from the start of the operation of the turbo compressor, and a stop means for stopping the water spray of the water spray nozzle until a predetermined time from the start of the operation. Immediately after the start of the operation of the compressor, the temperature of the casing and the like of the compressor is still low.
When the spray amount of water is determined based on the air flow rate or the required power as in the invention of the above-mentioned invention, the spray amount of water may become excessive and fine water droplets may remain. Therefore, a predetermined warm-up time is secured by the timer, and this is avoided.

[0013] The water spray nozzle may be arranged at an intermediate position of an impeller of the turbo compressor. This is because the air has not yet been sufficiently accelerated at the impeller entrance,
Since the temperature is not so high as to evaporate the water spray, water is sprayed at an intermediate position of the impeller where the temperature is equal to or higher than the vaporization temperature.

Further, the water spray nozzle may be arranged in an intercooler connected to the upstream side of the turbo compressor. Since the intercooler has relatively small vibration compared to the vicinity of the compressor, it is easy to take measures against the vibration of the water spray nozzle.

Further, the turbo compressor may be connected in a plurality of stages, and all or some of them may be provided with the water spray nozzle.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 shows an example in which the present invention is applied to a centrifugal compressor used as a compressed air supply source in a factory or the like. The centrifugal compressor 1 has an impeller 2 that is driven to rotate by a motor (not shown), a casing 3 that houses the impeller 2, a suction pipe 4 that guides air as intake air to the casing 3, and is discharged from the impeller 2. It has a diffuser 5 for decelerating air and converting it to pressure, and a scroll chamber 6 for rectifying the air discharged from the diffuser 5 and flowing it to the downstream side.

The suction pipe 4 on the suction side of the impeller 2 includes:
A water spray nozzle 7 for spraying water into fine water droplets is provided in the pipe 4. The water spray nozzle 7 is attached to a tip of a water pipe 8 to which a water pump (not shown) is connected.
The water pipe 8 is provided with a water amount control valve 9. Further, a temperature sensor 10 for measuring the temperature of the discharged fluid there is provided in an upstream portion of the diffuser 5 on the discharge side of the impeller 2. The diffuser 5 may be a vaneless type or a type with a vane.
0 may be provided in the scroll chamber 6.

The temperature sensor 10 and the water amount control valve 9 are connected to a control means 11. The control means 11 is a thermal indicator controller that controls the amount of water sprayed from the water spray nozzle 7 so that the temperature detected by the temperature sensor 10 reaches a preset target temperature. That is, if the temperature detected by the temperature sensor 10 is higher than the target temperature,
Is opened to increase the amount of water spray, and if the temperature detected by the temperature sensor 10 is lower than the target temperature, the water amount control valve 9 is closed to reduce the amount of water spray. For this control, feedback control using general proportional-integral control is employed. The adjustment of the water spray amount by the water amount adjustment valve 9 is performed by adjusting the opening of the water amount adjustment valve 9.

In the present embodiment, the target temperature is set to "saturation temperature of steam (saturated steam temperature) plus 5 degrees". However, this is merely an example, and in practice, it is sufficient that the temperature is equal to or higher than the “saturated steam temperature”. "Saturated steam temperature"
Is (the discharge side portion 1 where the temperature sensor 10 is installed)
Although the pressure fluctuates according to the magnitude of the pressure in 2), the pressure of the discharge side portion 12 fluctuates somewhat in the centrifugal compressor 1 used as a compressed air supply source in a factory or the like, but is substantially constant. It can be uniquely determined in advance based on the pressure.
Note that a pressure sensor may be provided in the discharge-side portion 12 to calculate an exact “saturated steam temperature” based on the pressure.

The reason why the target temperature is set to “saturated steam temperature plus 5 degrees” is to ensure that all the water sprayed on the suction side portion 13 is vaporized in the discharge side portion 12. That is, if the target temperature is set to “saturated steam temperature”, the water sprayed in the suction side portion 13 should just be vaporized in the discharge side portion 12 to be in a saturated steam state. If the pressure fluctuates slightly, the saturated steam temperature fluctuates, and fine water droplets may remain without being completely vaporized. Therefore, the target temperature is set to "saturated steam temperature plus 5 degrees" in consideration of a certain safety factor.

As described above, from the viewpoint of reliably vaporizing the sprayed water, the target temperature may be any number of times as long as the target temperature is equal to or higher than the “saturated steam temperature”. If so, the amount of sprayed water is reduced, and the cooling effect due to the heat of vaporization is reduced. Therefore, in this embodiment, the target temperature is set to "saturated steam temperature plus 5 degrees" in order to secure a certain cooling effect. This ensures reliable vaporization of the sprayed water,
It ensures a high level of cooling effect by the heat of vaporization.

When the temperature sensor 10 is installed in the scroll chamber 6, the air in the scroll chamber 6 is decelerated after being discharged from the impeller 2 to increase the pressure and the temperature. It is necessary to set the target temperature. That is, assuming that the target temperature when the temperature sensor 10 is installed in the discharge side portion 12 is “saturated steam temperature plus 5 degrees”, the target temperature when the temperature sensor 10 is installed in the scroll chamber 6 is “saturated steam temperature plus 5 degrees plus α ".

The operation of this embodiment having the above configuration will be described with reference to FIG.

The cycle of a normal centrifugal compressor without water spraying is, as shown by a broken line, an equal pressure suction 4 → 1 in the suction pipe 4, an adiabatic compression 1 → 2 in the impeller 2, and a cycle in the scroll chamber 6. It consists of equal pressure discharge 2 → 3, 1 →
The area surrounded by 2 → 3 → 4 is compression work, that is, required power. Further, the ideal compression process is isothermal compression 1 → 2 ′ obtained by performing cooling while compressing, as shown by the dashed line, and the required power at that time is 1 →
Although the area is surrounded by 2 '→ 3 → 4, it is impossible in reality.

In the present embodiment, fine water droplets sprayed on the upstream side of the impeller 2 are vaporized during the compression stroke, and the adiabatically compressed air is cooled by the heat of vaporization. Adiabatic compression 1 → 2 to isothermal compression 1 → 2 '
And the cooling compression stroke becomes 1 → 2 ″. Therefore, the required power of the centrifugal compressor according to this embodiment is 1 → 2 ″ → 3 →
4 which is clearly smaller than the area surrounded by the required power 1 → 2 → 3 → 4 of a normal centrifugal compressor without water spraying.

More specifically, in the initial stage of the cooling and compression process 1 → 2 ″ of the centrifugal compressor according to the present embodiment, since the fine water droplets sprayed from the nozzle 7 have not yet been vaporized and evaporated, the fine water droplets are transferred to the impeller 2. , The compression work (wasteful work) slightly larger than the adiabatic compression 1 → 2 is required, and this is the portion that protrudes to the right side from the adiabatic compression 1 → 2 indicated by the broken line. Increases and loses.

However, after that, in the middle stage of the cooling / compression process 1 → 2 ″, the fine water droplets start to evaporate, and the heat of vaporization cools the air during the adiabatic compression. In the left side of → 2, it approaches isothermal compression 1 → 2 ′, the compression work is reduced by that much, and the required power is reduced.As a result of the experiment, the centrifugal having the cooling compression stroke 1 → 2 ″ according to the present embodiment is shown. The power of the compressor has been confirmed to be 7% or more lower than that of a normal centrifugal compressor in which adiabatic compression 1 → 2 without water spray is performed.

Further, since the amount of water spray is controlled so that the temperature of the discharge side portion 12 of the impeller 2 becomes equal to or higher than the saturation temperature of water vapor, all the sprayed water is vaporized, which is caused by an excessive spray amount. Residual fine water droplets in the discharged air are avoided. That is, all the fine water droplets sprayed from the nozzle 7 are necessarily vaporized while passing through the impeller 2, and are not discharged to the discharge side portion 12 of the impeller 2. For this reason, the loss caused by accelerating the fine water droplets with the impeller 2 is reduced, and the required power is reliably reduced. In addition, since the discharge air free of the fine water droplets is obtained, its utility value increases.

Further, since the water spray amount is controlled so that the temperature of the discharge side portion 12 of the impeller 2 becomes the target temperature (saturated steam temperature plus 5 degrees), a predetermined water spray amount is secured.
Insufficient cooling due to too little water spray is also avoided. That is, if the target temperature is much higher than the saturated steam temperature,
Although the amount of water spray decreases and the cooling effect of the compressed air due to the heat of vaporization decreases, in the present embodiment, the target temperature is set to “saturated steam temperature plus 5 degrees”, so that the reliable vaporization of the sprayed water is performed. And the effect of cooling the compressed air by the heat of vaporization can be achieved at a high level.

In this embodiment, an example is shown in which the present invention is applied to a centrifugal compressor. However, the present invention may be applied to an axial compressor. Further, in this embodiment, an example is shown in which the present invention is applied to a centrifugal compressor used as a compressed air supply source in a factory or the like, but it may be applied to a compressor portion of a turbocharger used as an exhaust supercharger for ships. In this case, the amount of work on the turbine side is reduced, so that supercharging is possible even at low engine speeds where the amount of exhaust gas, which has not been obtained conventionally, is small.
Further, since fine water droplets do not mix with the pressurized intake air, the problem of rust inside the engine does not occur.

However, in the case of a marine turbocharger, the pressure fluctuation of the discharge side portion 12 is large, and the saturated steam temperature also fluctuates accordingly, so that the amount of water spray becomes excessive and fine water droplets are likely to remain. Therefore, a pressure sensor (not shown) is provided in addition to the discharge-side portion 12 provided with the temperature sensor 10 shown in FIG. 1, and based on the pressure obtained by the pressure sensor, the exact "saturated steam temperature" at that time is determined. By calculating and comparing the “saturated steam temperature” with the detected temperature obtained by the temperature sensor 10, it is possible to cope with the pressure fluctuation of the discharge-side portion 12 that changes every moment.

Another embodiment is shown in FIGS.

As shown in FIG. 3, in this embodiment, two centrifugal compressors 1 of the previous embodiment are connected in series, and a suction control valve 14 is provided upstream of the first stage compressor 1a. An intercooler 15 is interposed between the first-stage compressor 1a and the second-stage compressor 1b, and an aftercooler 1 is provided downstream of the second-stage compressor 1b.
6 is a water spray type two-stage compression system. In addition, components having the same functions as those of the previous embodiment are denoted by the same reference numerals, and description thereof is omitted.

Now, as shown by a broken line in FIG. 4, the cycle of the two-stage compression system in which the water spray is not performed includes the equal-pressure suction 6 → 1 in the suction pipe 4 and the adiabatic compression 1 in the first-stage compressor 1a. → 2 and equal pressure cooling 2 by intercooler 15
→ 3, adiabatic compression 3 → 4 in the second stage compressor 1b,
An area surrounded by 1 → 2 → 3 → 4 → 5 → 6 composed of equal pressure discharges 4 → 5 in the aftercooler 16 is compression work, that is, required power. Also, the ideal compression stroke is
As shown by the dashed line, isothermal compression 1 → 3 → 4 ′ obtained by cooling while compressing, the required power at that time is the area enclosed by 1 → 3 → 4 ′ → 5 → 6. But it is not possible in reality.

In this embodiment in which water is sprayed, as described in the previous embodiment, fine water droplets sprayed on the upstream side of the impeller of each of the compressors 1a and 1b are vaporized during the compression stroke, and the vaporized heat causes Since the air to be adiabatically compressed is cooled, the adiabatic compression 1 → 2, 3 → 4 when water spraying is not performed approaches the isothermal compression 1 → 3, 3 → 4 ′, respectively, and the cooling compression process 1 →
2 ″, 3 → 4 ″. For this reason, 2 according to the present embodiment
The required power of the stage compression system is 1 → 2 ″ → 3 → 4 ″ → 5
→ The area enclosed by the area surrounded by 6 is the area surrounded by the required power of the normal two-stage compression system without water spray (1 → 2 →
(Area surrounded by 3 → 4 → 5 → 6). According to experiments, a power reduction of 7% or more has been confirmed.

The compressors 1a and 1b of each stage are sprayed because the temperature of the discharge side of the impeller of each compressor 1a and 1b is controlled to be equal to or higher than the saturation temperature of steam by the control means 11 and 11. All of the water that has been vaporized is vaporized, so that fine water droplets are prevented from remaining due to excessive spraying. In addition, since the temperature on the discharge side is controlled to be equal to the target temperature (saturation temperature of water vapor plus 5 degrees), insufficient cooling due to an insufficient amount of water spray is also avoided. These points are the same as in the previous embodiment. As a result, for the compressors 1a and 1b at each stage, the reliable vaporization of the sprayed water and the cooling effect of the compressed air by the heat of vaporization can be achieved at each stage at a high level.

Another embodiment is shown in FIGS.

As shown in FIG. 5, this embodiment corresponds to FIG.
The receiver tank 19 is connected to the discharge pipe 17 of the previous embodiment via a check valve 18 as shown in FIG.
A branch pipe 21 having a blow-off control valve 20 is connected to the upstream side of the air conditioner, and a load operation in which the suction control valve 14 is opened and the blow-off control valve 20 is closed is performed. It is configured to be able to switch between load operation and load operation. Note that the suction control valve 14 that is closed during the no-load operation is not completely closed, and a flow rate that can avoid surging is secured.

The present embodiment is characterized in that a detecting means 22 for detecting whether the above-described two-stage compression system is in a load operation or a no-load operation, and the water spray nozzle 7 in the no-load operation.
(See FIG. 1). The detecting means 22 is connected to the suction control valve 14 and the blow-off control valve 20, and detects whether the load operation or the no-load operation is performed based on the open / close state of each of the valves 14, 20. That is, if the suction control valve 14 is opened and the blow-off control valve 20 is closed, load operation is detected, and if the suction control valve 14 is closed and the blow-off control valve 20 is open, no-load operation is detected. .

When the no-load operation is detected by the detecting means 22, the stopping means 23 completely closes the water amount adjusting valves 9, 9 to reduce the amount of water spray to zero so that cooling by water spray is not performed. Things. The detecting means 22 and the canceling means 23 are actually constituted by a program (ON / OFF signal) written in the computer. Since the other configuration is the same as that of the previous embodiment, the components having the same functions are denoted by the same reference numerals and the description thereof will be omitted.

The two-stage compression system has a cycle indicated by a dashed-dotted line 24 in FIG. 6 during load operation and a cycle indicated by a solid line 25 in FIG. 6 during no-load operation. Therefore, the compression work (required power) during the load operation is the cycle area indicated by the dashed line 24 in FIG. 6, and the compression work (required power) during the no-load operation is the cycle area indicated by the solid line 25 in FIG. . Comparing the two, the required power during no-load operation is extremely smaller than the required power during load operation.

As described above, during no-load operation, since the required power is extremely small in the first place, the power reduction effect by cooling the water spray is small. Therefore, in the present embodiment, the water spray is stopped during the no-load operation, thereby simplifying the control. If the small required power during the no-load operation is further reduced by water spraying, a very small amount of water may be sprayed in accordance with the cycle of the no-load operation indicated by the solid line 25 in FIG. In this case, since a single type of water amount control valve 9 cannot finely control the water amount to a very small amount, another solenoid valve for a very small amount is provided.

Another embodiment is shown in FIG.

As shown in FIG. 7, this embodiment has basically the same configuration as that shown in FIG. 3, except that a flow sensor 26 is provided in place of the temperature sensor 10 and the flow sensor 2 is provided.
A determination means 27 for determining the amount of water spray from the nozzle 7 (see FIG. 1) based on the flow rate detected at 6 is provided.
9 is controlled.

This embodiment focuses on the fact that the temperature (heat amount) on the discharge side of the impellers of the compressors 1a and 1b, which is a parameter in the embodiment of FIG. 3, is proportional to the flow rate of air passing through the compressors 1a and 1b. By spraying a predetermined ratio of water based on the air flow rate, it is possible to avoid the residual phenomenon of fine water droplets due to overspray and the insufficient cooling phenomenon due to underspray beforehand. Things.
Specifically, the water spray amount (weight) is set to about 0.5 to 2% of the air flow rate (weight).

The location of the flow sensor 26 is shown in FIG.
The first stage compressor 1a is not limited to the discharge pipe 17 as shown in FIG.
It may be a pipe 28 between the first stage compressor 1b and the intake pipe 4. This is because the air flow rate does not change everywhere.
Further, since the heat quantity is the product of the flow rate and the temperature, both the temperature sensor 10 shown in FIG. 3 and the flow rate sensor 26 shown in FIG.
The amount of water spray may be feedback controlled using the amount of heat obtained by multiplying by the detected flow rate as a parameter.

Another embodiment is shown in FIG.

As shown in FIG. 8, this embodiment has basically the same configuration as that shown in FIG. 3, except that the temperature sensor 10 is replaced with a common drive motor for each compressor 1a, 1b. A power sensor 30 for detecting a required power of 29;
The nozzle 7 based on the power detected by the power sensor 30
The only difference is that a determining means 31 for determining the amount of water spray from (see FIG. 1) is provided, and the water amount adjusting valves 9, 9 are controlled so that the amount of water spray determined by the determining means 31 is obtained. I have. The compressors 1a and 1b of each stage are driven by a single motor 29 in conjunction with each other via a gear train (not shown).

In this embodiment, the temperature (heat amount) on the discharge side of the impellers of the compressors 1a and 1b, which is a parameter in the embodiment of FIG. 3, is proportional to the flow rate of air passing through the compressors 1a and 1b. The flow rate is the drive motor 2 of the compressors 1a and 1b.
It is made by paying attention to the fact that it is proportional to the required power of No. 9, and by spraying a predetermined ratio of water based on the required power, the residual phenomenon of fine water droplets due to excessive spraying and insufficient cooling due to insufficient spraying This is to avoid the phenomenon beforehand.

The determining means 27, 31 (essentially a program written in the computer) of the embodiment shown in FIGS. 7 and 8 include a timer for measuring the time from the start of operation of the compressors 1a, 1b. A stopping means for stopping the water spray of the water spray nozzle 7 (see FIG. 1) by fully closing the water amount adjusting valves 9 and 9 for a predetermined time (for example, three minutes) from the start of operation may be incorporated. These timers and stop means are substantially programs written in a computer.

Immediately after the start of the operation of the compressors 1a and 1b, since the temperature of the casing 3 (see FIG. 1) of the compressors 1a and 1b is still low, the air as in the embodiment shown in FIGS. When the spray amount of water is determined based on the flow rate and the required power, the water amount assumed to be the saturated steam temperature before the discharge side portion 12 shown in FIG.
Since it is determined and supplied according to 7, 31, the spray amount of water becomes excessive, and fine water droplets may remain. Therefore, a predetermined warm-up time (for example, 3 minutes) is secured by the timer and the canceling means, and the predetermined warm-up time is avoided.

FIG. 9 shows that the water spray nozzle 7 is connected to the centrifugal compressor 1.
At an intermediate position of the impeller 2. This is because the air has not yet been sufficiently accelerated at the inlet position of the impeller 2 and the temperature has not risen enough to vaporize the water spray, so that water is sprayed to the intermediate position of the impeller 2 where the temperature is equal to or higher than the vaporization temperature. It was made. This allows
The fine water droplets sprayed from the nozzle 7 are quickly vaporized, and the amount of wasteful work caused by accelerating the fine water droplets by the impeller 2 is smaller than that in FIG.
That is, the area of the portion where the cooling compression stroke 1 → 2 ″ shown by the solid line in FIG. 2 protrudes to the right from the adiabatic compression stroke 1 → 2 shown by the broken line is reduced, and the compression work, that is, the required power, is reduced accordingly.

FIG. 10 shows a configuration in which the water spray nozzle 7 is disposed in a pipe 33 between the suction filter 32 and the suction control valve 14 and in the intercooler 15. In this case, the pipe 33 and the intercooler 15 are connected to the impeller 2 shown in FIG.
Because the vibration during operation is smaller than near the immediate upstream of
Countermeasures against vibration of the water spray nozzle 7 are facilitated.

The centrifugal compressors 1, 1a, 1b shown in FIGS. 1 to 10 are not limited to one stage or two stages, but may be connected in three or more stages. Further, the water spray nozzle 7 may be provided on all or some of them.

[0056]

As described above, according to the water spray device for a turbo compressor according to the present invention, the spray amount of water can always be properly controlled, and the compression work, that is, the required power can be reliably reduced. .

[Brief description of the drawings]

FIG. 1 is a diagram illustrating a water spray device for a turbo compressor according to an embodiment of the present invention.

FIG. 2 is a cycle diagram of the turbo compressor.

FIG. 3 is an explanatory view of a water spray device for a turbo compressor according to another embodiment.

FIG. 4 is a cycle diagram of the turbo compressor.

FIG. 5 is an explanatory view of a water spray device for a turbo compressor according to another embodiment.

FIG. 6 is a cycle diagram of a load operation and a no-load operation of the turbo compressor.

FIG. 7 is an explanatory view of a water spray device for a turbo compressor according to another embodiment.

FIG. 8 is an explanatory view of a water spray device for a turbo compressor according to another embodiment.

FIG. 9 is an explanatory view showing a modified embodiment of the installation location of the water spray nozzle.

FIG. 10 is an explanatory view showing another modified embodiment of the installation location of the water spray nozzle.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Centrifugal compressor as a turbo compressor 7 Water spray nozzle 10 Temperature sensor 11 Control means 12 Discharge side part 13 Suction side part 15 Intercooler 22 Detecting means 23 Stopping means 26 Flow rate sensor 27 Determining means 30 Power sensor 31 Determining means

Claims (8)

[Claims] 1. A water spray nozzle provided on a suction side of a turbo compressor, a temperature sensor provided on a discharge side of the turbo compressor, and a temperature detected by the temperature sensor is set to be equal to or higher than a saturation temperature of steam. Control means for controlling the water spray amount of the water spray nozzle so as to reach the target temperature. 2. The turbo compression system according to claim 1, further comprising: detection means for detecting whether the turbo compressor is in a load operation or a no-load operation, and a stop means for stopping the water spray of the water spray nozzle during the no-load operation. Water spray device for the machine. 3. A water spray nozzle provided on a suction side of a turbo compressor, a flow sensor for detecting an air flow passing through the turbo compressor, and a water spray based on the air flow detected by the flow sensor. A water spray device for a turbo compressor, comprising: a determination unit for determining a water spray amount of the nozzle. 4. A water spray nozzle provided on a suction side of a turbo compressor, a power sensor for detecting a required power of a motor for driving the turbo compressor, and water based on the power detected by the power sensor. Determining means for determining a water spray amount of the spray nozzle; a water spray device for a turbo compressor. 5. The turbo compressor according to claim 3, further comprising a timer for measuring a time from the start of operation of the turbo compressor, and a stop means for stopping water spray of the water spray nozzle until a predetermined time from the start of operation. Water spray device for turbo compressor. 6. The turbo compressor is connected in multiple stages,
The water spray device for a turbo compressor according to any one of claims 1 to 5, wherein the water spray nozzle is provided on all or some of them. 7. The water spray device for a turbo compressor according to claim 1, wherein the water spray nozzle is disposed in an intercooler connected to an upstream side of the turbo compressor. 8. The water spray device for a turbo compressor according to claim 1, wherein the water spray nozzle is disposed at an intermediate position of an impeller of the turbo compressor.