JP2001107834A - Operating method of water-turbine-driven comprfssor and water-turbine-driven compressor for executing this operating method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an operating method of a water turbine driving compressor capable of stably operating the compressor at a desired rotational speed with a rise up early at starting time and the water turbine driving compressor for executing this operating method. SOLUTION: An electric motor 10 is connected to an input side of a compressor main unit 50, also a water turbine 40 is connected through a clutch means 62 of centrifugal clutch, electromagnetic clutch, etc., outputs of the electric motor 10 and the water turbine 40, synthesized, can be input to the compressor main unit 50. A compressor 1 is started by the electric motor 10, also when a rotational speed of the water turbine 40 is increased to a preset rotational speed or more, for instance, like a rated rotational speed or more of the electric motor 10, the water turbine 40 and the compressor main unit 50 are connected by the clutch means 62, and an output of the water turbine 40 is input to the compressor main unit 50.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method of operating a water turbine driven compressor using a water turbine as a drive source of a compressor body, and a water turbine driven compressor for carrying out the operation method.

[0002]

2. Description of the Related Art In a turbine driven compressor that uses a water turbine instead of a motor or an engine as a prime mover for driving a compressor body that performs a fluid compressing action, an input between a shaft of the turbine and a compressor body is used. The shaft is connected via a power transmission device, and the output of the water turbine is transmitted to the compressor body.

[0003] In such a water turbine driven compressor,
The output of the turbine driving the compressor body varies depending on the head and amount of water introduced into the turbine, and when the head is constant, the output of the turbine can be increased or decreased by increasing or decreasing the amount of water. Therefore, a valve for adjusting the amount of water introduced into the turbine is provided in the hydraulic line of the turbine, and the output of the turbine is adjusted by adjusting the opening of the valve to adjust the amount of water introduced into the turbine. Is going.

On the other hand, the compressor body to which the power generated by the turbine as described above is input as the driving power is connected to the shaft of the turbine and acts as a load on the turbine. It increases or decreases depending on the relationship between the amount of intake air introduced into the machine body and the discharge side pressure.
For example, when the suction valve provided in the suction passage of the compressor body is open, when the rotation speed of the compressor body is increased to increase the amount of intake air, the driving power, that is, the load increases, and vice versa. Meanwhile, when the rotational speed of the compressor body is reduced to reduce the amount of intake air, the load is reduced.

[0005] Even if the intake air amount does not fluctuate while the rotation speed of the compressor body is kept constant, if the consumption of compressed air decreases, the pressure on the discharge side increases and the load increases.
When the consumption of the compressed air increases, the discharge side pressure decreases and the load also decreases.

As described above, the load on the turbine varies depending on the operating condition of the compressor body. Therefore, when the water head and the amount of water introduced into the turbine are kept constant and the output of the turbine is kept constant, the turbine and the compressor are fixed. The rotation speed of the main unit fluctuates. For example, if the load on the turbine increases due to an increase in the intake air amount of the compressor body or an increase in the discharge side pressure of the compressor body,
When the rotation speed of the turbine and the compressor body decreases, and the load on the turbine decreases due to a decrease in the intake air amount of the compressor body and a decrease in the pressure in the discharge chamber, the turbine and the compressor body The rotation speed increases.

[0007] Such increase and decrease of the driving power of the compressor body,
That is, in order to prevent a change in the number of revolutions of the compressor due to an increase or decrease in the load on the turbine, the output of the turbine is increased or decreased in accordance with the increase or decrease in the load,
It is necessary to balance the output of the turbine. Therefore, in the conventional water turbine driven compressor, the amount of water introduced into the water turbine is adjusted by adjusting a valve provided in the hydraulic line according to the increase or decrease of the load by the compressor body, and the output of the water turbine is increased. Adjustments are made to keep the number of revolutions of the compressor constant according to the increase and decrease of the load.

[0008]

In the above-described hydraulic turbine driven compressor, when a valve provided in a hydraulic line of the hydraulic turbine is rapidly opened and closed, a dam is rapidly generated with respect to an impeller of the hydraulic turbine. The impact pressure of water stored in a water source such as a water source or a reservoir may be damaged due to the impact, and the height of the water from the water source and the valve head of the valve to which the pressure head is added suddenly open and close. Requires a lot of energy,
Further, the valve that controls the introduction of water into the water turbine is configured to gradually operate in the opening direction or the closing direction, for example, because sudden opening and closing of the valve may lead to damage of the valve itself. Therefore, the output of the water turbine fluctuates gradually with the change in the amount of water introduced by the valve, and it takes a relatively long time from the start to the time when the compressor main body is operated at a desired rotation speed.

Further, when the compressor body is operated at a desired rotational speed, the consumption of the compressed air increases and decreases, and the difference between the output of the water turbine and the driving power required by the compressor body occurs. Even when the above occurs, a change in the output of the water turbine adjusted by the valve that operates gradually as described above can immediately follow a change in the driving power of the compressor body that causes a relatively rapid change. It was impossible.

Therefore, when the load generated by the compressor body is reduced, the output of the turbine becomes excessive with respect to the load, and the number of revolutions of the compressor is extremely increased, resulting in a so-called "overrun" state. In addition, when the load generated by the compressor body becomes large, the output of the turbine becomes insufficient for this load, and a so-called “stall” state occurs in which the number of revolutions of the compressor extremely decreases, and the compressor body becomes There are problems that an excessive load is generated and that it takes a long time for the compressor to return to the rated operation.

Further, the output of the water turbine is determined by the water head as described above, and this water head differs for each facility where the water turbine drive compressor is installed, and for each time. In particular, when the amount of water stored in a dam or a reservoir, which is a water source, is reduced, for example, during the summer or dry season, the drive power required by the compressor body may not be output only by the water turbine.

The present invention has been made in order to solve the above-mentioned drawbacks in the prior art, and it has been made possible to start the engine without excessive load on the impeller of a water turbine, a valve provided in a hydraulic line, and the like. The time required to reach rated operation can be shortened as compared to conventional turbine driven compressors, and the power input to the compressor main body is immediately changed in response to the load fluctuation caused by the compressor main body. Can fluctuate,
Therefore, there is no adverse effect such as overrun or stall, and further, even in a case where the water storage amount of the water source is not sufficient, such as in a summer season or a dry season, a water turbine driven compressor capable of operating the compressor at a desired rotation speed. It is an object of the present invention to provide an operation method of a water turbine and a water turbine driven compressor for implementing the operation method.

[0013]

In order to achieve the above object, a method of operating a water turbine driven compressor and a water turbine driven compressor according to the present invention comprise a compressor main body 50 and a water turbine driving the compressor main body 50. In the water turbine drive type compressor 1 provided with the compressor 40, the electric motor 10 is connected to the input side of the compressor main body 50, and the clutch means 62 such as a centrifugal clutch, an electromagnetic clutch, etc.
The output of the electric motor 10 and the output of the water turbine 40 are combined so that the output can be input to the compressor main body 50, and the rotation speed of the water turbine 40 is set at a predetermined rotation. The output of the water turbine 40 is input to the compressor main body 50 via the clutch means 62 when the rotation speed is equal to or more than the rated speed of the electric motor 10, for example.

As a method of simultaneously connecting the electric motor 10 and the water wheel 40 to the compressor main body 50, one end 11a of the rotating shaft 11 of the electric motor 10 is connected to the water wheel 40 via the clutch means 62 and the electric motor 10 Rotating shaft 11
May be connected to the input side of the compressor main body 50, and the power transmission means 60 for transmitting the output of the water turbine 40 and the electric motor 10 to the compressor main body 50 has two input shafts 64.
a, 64b, etc., two input shafts are provided on the input side of the compressor body 50, and the motor 10 is connected to one of the input shafts 64b, and the other of the input shafts 64a is provided.
Alternatively, the water turbine 40 may be connected via the clutch means 62.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The construction of a water turbine driven compressor according to the present invention will be described below with reference to the accompanying drawings.

[Overall Configuration of Compressor] FIG. 1 shows the overall configuration of a water turbine driven compressor according to the present invention. A compressor 1 shown in FIG. 1 rotates a water turbine 40 provided therein by a water flow introduced from a water source such as a dam or a reservoir, and a compressor main body 5.
0 is a water wheel drive type compressor that compresses a fluid such as air by driving the water wheel 40 and the water wheel 4
The electric motor 10 replenishes the output of 0 or acts as a load on the water turbine, the power transmission means 60 for transmitting the rotational power of the water wheel 40 and the electric motor 10 to the compressor main body 50, and is driven via the power transmission means 60. Compressor body 50
And various pipes and parts connected to the compressor body 50,
Includes accessories.

[Water Turbine] A water turbine 4 which is a driving source of the compressor 1
Numeral 0 is a power source for the compressor body 50 by converting fall energy of water taken from a water source such as a dam or a reservoir into rotational energy, and is used as a power source of the compressor body 50.
And a shaft 44 rotatably fixed to the impeller, and the impeller 42 is rotatably disposed in a water turbine chamber 46 into which water such as a dam is introduced.

The water turbine room 46 has an inlet 46a constituting a hydraulic line communicating with a water source, and a drainage for introducing water into the water turbine room 46 to discharge water after rotating the water turbine to the outside of the machine. The mouth 46b is provided. Of these, the inlet 46a is
A water source such as a dam or a reservoir is communicated via a pipe and a valve, and a drain port 46b is opened, for example, outside the machine so that water passing through the water turbine room 46 can be discharged.

Accordingly, the valve is opened and closed to open the water turbine chamber 46.
The water turbine 40 can be started or stopped by starting the introduction of water into or stopping the introduction of water into the inside of the water turbine chamber 46 by adjusting the valve opening. The rotation speed of the water wheel 40 can be adjusted by adjusting such factors.

In this embodiment, an electric valve MV is used as a valve for controlling the introduction of water into the water turbine chamber 46, and the flow of water is controlled by opening and closing and adjusting the opening of the electric valve MV. , The number of rotations can be automatically adjusted.

As the electric valve MV, various types of known electric valves MV can be used. Further, for example, a known thermal overcurrent circuit or the like is incorporated in a drive circuit of the electric valve MV, and, for example, foreign matter is caught. Alternatively, an electric valve configured to stop the motor of the electric valve MV when the motor of the electric valve MV is restrained by water pressure or the like and an unnecessary load is applied may be used.

Further, in the water turbine driven compressor 1 of the present embodiment, as an example, the effective head is 45.0 m and the flow rate is 9.5.
At m ³ / min, about 45 kW of power is generated.

[Power Transmission Means] The power generated by the water turbine 40 configured as described above is input to the compressor body via the power transmission means 60.

The power transmission means 60 for transmitting the output generated by the water turbine 40 to the compressor main body 50 has any structure as long as it can transmit the torque of the shaft 44 of the water turbine 40 to the input shaft 51 of the compressor main body 50. In this embodiment, the power transmission means 60 is constituted by two speed increasing devices 64 and 66 connected by a shaft coupling 68.

[Compressor Body] As described above, as the compressor body 50 driven by the water turbine 40 via the power transmission means 60, various types of compressor bodies can be used.
The format is not limited. As an example, the compressor main body 50 of the present embodiment shown in FIG. 1 is introduced into a compression action space formed by meshing the male rotor and the female rotor by the male rotor and the female rotor meshing and rotating. It is a known screw compressor configured to be able to compress air. As the screw compressor, any type may be used, such as a type that uses oil for sealing and cooling the compression working space, a type that uses water instead of oil, and a type that does not inject oil or water at all. In addition, various types of compressors other than the screw compressor, such as a scroll type compressor and a reciprocating type compressor, can be used, and the type of the compressor body 50 is not limited to the embodiment.

A suction valve 53 and an air filter 54 are provided at an intake port 52 of a compressor body 50 of the present embodiment described as a screw compressor, and a discharge port of the compressor body 50 is connected through a discharge pipe 72. For example, it is connected to a pneumatic working machine (not shown).

The compressor body 50 is cooled by a cooling medium such as cooling water to cool the compressor body 50 which has been heated by the compression work, and lubricating oil is injected into the compressor body. Smooth operation is ensured.

Further, the compressor main body 50 has an opening / closing mechanism for opening and closing a suction valve 53 provided at an intake port 52 of the compressor main body, and a discharge port 5 for the compressor main body.
An air discharge valve 73 for discharging compressed air in a discharge pipe 72 connected to the compressor 5 is provided so that the operation of the compressor body 50 can be switched from a full-load operation state to a no-load operation state.

As the opening / closing mechanism of the suction valve 53, various known structures can be used. In the present embodiment, a hydraulic cylinder 74 and a hydraulic cylinder 74 are used as the opening / closing mechanism of the suction valve 53. Primary chamber 74a of hydraulic cylinder 74
And an electromagnetic valve SV for controlling the introduction and discharge of the hydraulic oil to and from the secondary chamber 74b.

The secondary chamber 74 of the hydraulic cylinder 74
The pipe 81 communicated with b is provided with an air release valve 73 that operates using the hydraulic pressure in the pipe 81 as pilot pressure, and is configured such that when the suction valve 53 closes, the air release valve 73 opens. ing.

In this embodiment, the compressor body 5
A circulation circuit of the lubricating oil for 0 is used as a hydraulic circuit for driving the hydraulic cylinder 74 and the discharge valve 73 which are the above-described opening and closing mechanism of the suction valve.

[Lubricating oil circulation circuit and intake valve opening / closing mechanism]
An example of an opening / closing mechanism of the suction valve 53 according to the present embodiment in which a lubricating oil circulation circuit is used as a part of a hydraulic circuit that opens and closes the suction valve 53 will be described with reference to FIG. A lubrication port 56 for lubricating oil is provided as described above, and the lubrication port 56 is connected to a lubricating oil supply source via pipes 82 and 83.

In this embodiment, of the speed increasing devices 64 and 66 provided as the above-described power transmission means 60, the oil is contained in the casing of the second speed increasing device 66 disposed on the compressor body 50 side. A reservoir 67 is formed, and the oil reservoir 67 is used as a supply source of the lubricating oil.

A hydraulic pump 90 is provided in a pipe 82 connected to the above-mentioned oil sump 67. By driving the hydraulic pump 90, the lubricating oil in the oil sump 67 is circulated in a lubricating oil circulation circuit. Is sucked into. The hydraulic pump 90 may have its own drive source such as an electric motor, but in this embodiment, the hydraulic pump 90 receives power from the second speed increasing device 66. It is configured to work.

On the discharge side of the hydraulic pump 90, the pipe 82 is branched into two branches, and one of the branches 83 is connected to an oil inlet 56 of the compressor body via an oil cooler 92. . Therefore, the lubricating oil passing through the pipe 83 is introduced into the compressor main body 50 after being cooled by the oil cooler 92.

The other branched pipe 84 communicates with a primary chamber 74a of a hydraulic cylinder 74 which forms an opening / closing mechanism of a suction valve 53 provided at an intake port 52 of the compressor main body 50. Piping 81 communicated with the chamber 74b
Is connected to an oil sump 67 of the speed increasing device 66. The lubricating oil discharged from the oil discharge port 57 after being circulated in the compressor main body 50 is merged with the return pipe 81 connected to the speed increasing device 66, and the lubricating oil again flows into the second speed increasing device 66. It is configured to circulate in the oil sump 67 formed in the oil reservoir 67.

The lubricating oil circulation circuit 8 communicated with the primary chamber 74a and the secondary chamber 74b of the hydraulic cylinder 74.
1 and 84 are connected to a solenoid valve SV which is a four-port two-position switching valve, and when the position of the solenoid valve SV is switched, the primary chamber 74a and the secondary chamber 74b of the hydraulic cylinder 74 as shown by arrows in FIG. It is configured to be able to switch the introduction and discharge of hydraulic oil to the opposite direction. Accordingly, the position of the solenoid valve SV causes the shaft of the hydraulic cylinder 74 to reciprocate to open and close the suction valve 53.

The secondary chamber 74 of the hydraulic cylinder 74
b is branched between the hydraulic cylinder 74 and the solenoid valve SV, and the branched pipe 85
Is in communication with a pilot chamber of an air release valve 73 that communicates with the discharge pipe 72. In this way, for example, when the amount of air used by a pneumatic working machine (not shown) decreases and the pressure in the discharge pipe 72 rises to 0.69 Mpa, for example, the pressure is increased by a pressure switch PS2 provided in the discharge pipe 72, for example. Upon detection, the solenoid valve SV is switched, the suction valve 53 is closed by the hydraulic cylinder 74, and the air release valve 73 is opened to release the compressed air introduced into the discharge pipe 72 to the atmosphere to operate the compressor in the no-load operation. State.

Conversely, when the pressure in the discharge pipe 72 drops to 0.59 MPa as an example, this pressure drop is detected by the pressure switch PS2, and the solenoid valve SV is switched to open the suction valve 53 and release the pressure. The air valve 73 is closed to perform load operation.

[Cooling Medium Circulation System] In the compressor main body 50 having the above-described structure, a cooling medium inlet 58 of the compressor main body 50 is further provided with a pipe extending from a cooling medium supply source (not shown). 86 is connected, and a cooling medium such as cooling water is introduced into the compressor main body 50 through the pipe 86.

The compressor body 50 has a drain port 59 for discharging the cooling medium circulated inside the compressor body 50, and the cooling medium discharged through the drain port 59 is connected to a pipe 87. Is discharged out of the machine. In the present embodiment, after circulating through the compressor body 50 and exchanging heat as described above, the cooling medium discharged from the drain port 59 is introduced into the aftercooler 93 and the precooler disposed in the discharge pipe. And it is used for cooling the compressed air discharged from the compressor main body 50.

The cooling medium after cooling the compressor body 50 and / or the cooling medium introduced from the introduction source of the cooling medium is supplied to the oil cooler formed in the pipe 83 forming the above-described lubricating oil circulation circuit. It is introduced at 92 and is used for cooling lubricating oil.

As described above, the cooling medium that has cooled the compressor body 50 and the devices provided around the compressor body 50 is cooled, for example, by passing it through a radiator or a cooling tower (not shown) and then cooling it again. The cooling medium may be circulated to the introduction source of the medium and used for cooling the compressor body 50 and other devices. The used cooling medium may be discharged outside the apparatus, and a new cooling medium may be sequentially introduced. The compressor body 50 and its peripheral devices may be configured to be cooled.

In order to circulate the cooling medium in the circulation circuits 86, 87 and 88, for example, similarly to the hydraulic pump 90 used for circulating the lubricating oil, the speed increasing device 6 is used.
4, 66, the water wheel 40, a pump or the like that operates in conjunction with the compressor body 50 may be used.

Each component of the compressor 1 is housed in a soundproof box provided with a door that can be opened and closed to prevent noise during operation of the compressor 1 from leaking to the outside. Have been.

Further, a ventilation fan 96 for circulating the air inside the soundproof box by releasing the air inside the soundproof box and introducing the outside air is provided in the soundproof box surrounding each device as described above. The heat generated in the soundproof box by the operation of the device can be released outside the device.

[Electric Motor] In the water turbine driven compressor constructed as described above, the power transmission means 60
0 and the electric motor 10 are connected.

In the embodiment shown in FIG. 1, a so-called "double shaft type" motor 10 having both ends 11a and 11b of a rotating shaft 11 protruding from a casing of the motor 10 is used as the motor 10. One end 11a of ten rotating shafts
To the shaft 4 of the water turbine 40 via a centrifugal clutch 62.
4 and the other end 11b of the rotating shaft 11 is connected to the input shaft of the power transmission means 60 via a shaft coupling.

As the electric motor 10, it is preferable to use a constant-speed electric motor which does not change speed or changes little in speed with respect to a change in load torque when the voltage and the frequency are constant. A synchronous motor, a DC shunt motor, and a car A type induction motor or the like is used as the motor in the present invention.

In the present embodiment, a four-pole motor is
Driving at a power frequency of 0 Hz, the synchronous speed of the motor is 1,
800 min ^-1 and rated speed of 1,740 min ^-1 are obtained.

The centrifugal clutch 62, which connects the shaft 44 of the water wheel 40 and the rotating shaft of the electric motor, operates when the shaft 44 of the water wheel 40 reaches a predetermined number of rotations. For example, the lining of the centrifugal clutch 62 is attached to the shaft 44 of the water wheel 40, and the drum of the centrifugal clutch 62 is attached to the rotating shaft 11 of the electric motor 10.

In this embodiment, the rotation speed of the water turbine 40 is equal to the rated rotation speed of the electric motor 10, for example, 1,740.
The shaft 44 of the water wheel 40 is connected to the rotating shaft 11 of the electric motor 10 when the rotation speed reaches min ⁻¹ , and the connection between the two can be released when the rotation speed is less than the rotation speed.

In the water turbine driven compressor of the present invention provided with the electric motor 10 as described above, when starting the compressor 1, the electric motor 10 is first started, and the electric motor 10 Input driving power.

The introduction of water into the water turbine 40 is started at the same time as the start of the electric motor 10 or after the start of the electric motor 10. When the input of power to the compressor body 50 by the electric motor 10 is started, the rotation speed of the water wheel 40 is reduced. The rated speed of the electric motor 10 does not reach and the centrifugal clutch 62
The zero rotation shaft 11 and the shaft 44 of the water wheel 40 are in a separated state.

When the driving power of the compressor main body 50 is input by the motor 10, the rise time of the motor 10 up to the rated rotation speed is relatively short. Up to the number of revolutions. On the other hand, the rotation speed of the water turbine 40, whose rise time is relatively slow, gradually increases after the motor 10 reaches the rated rotation speed, and the rotation speed of the turbine 10 reaches the rated rotation speed of the motor 10. , The centrifugal clutch 62 operates to connect the shaft 44 of the water wheel 40 and the rotating shaft 11 of the electric motor 10.

As an example, the centrifugal clutch 62 used in this embodiment has a rotation speed of the water wheel 40 of about 1,7.
At about 00 min ^−1, the lining of the centrifugal clutch 62 attached to the shaft 44 of the water wheel 40 gradually starts to contact the drum attached to one end 11 a of the rotating shaft 11 of the electric motor 10 by centrifugal force, Electric motor 1
The configuration is such that the shaft of the water turbine and the rotating shaft of the electric motor are completely connected at 1,740 min ⁻¹ , which is the rated speed of 0. In this way, the power of the water turbine 40 is input to the compressor main body 50 via the electric motor 10, and when the rotation speed of the water turbine 40 is increased to the rated rotation speed of the electric motor 10, the compressor main body 50 is driven by the power of the water turbine 40. The load on the electric motor 10 due to the rotation is reduced. Therefore, the electric motor 10 is operated with almost no load, and the power consumption by the electric motor 10 is extremely small.

As described above, when the compressor 1 is operated at a predetermined rotation speed, the power generated by the water turbine 40 and the load generated by the compressor body 50 are balanced, and the compressor 1 It is operated in a stable state.

Due to the consumption of compressed air, etc.,
When the pressure on the discharge side decreases, the power consumed by the compressor main body 50 decreases, so that the load on the water turbine 40 is reduced, and the balance between the power generated by the water turbine 40 and the power consumed by the compressor main body 50 is reduced. Collapsed, watermill 40
The compressor 1 tries to increase its rotation even when the amount of water introduced into the compressor is constant and does not change.

However, the electric motor 10 is disposed between the shaft 44 of the water wheel 40 and the input shaft of the compressor body 50, and the shaft 44 of the water wheel 40 and the rotating shaft 1 of the electric motor 10 are arranged.
1 is connected by the centrifugal clutch 62, so that even when the load on the compressor main body 50 is reduced, the electric motor 10 becomes a load and an excessive increase in the rotation speed of the water turbine 40 is suppressed. That is, the motor 10 does not rotate beyond the synchronous rotation speed as long as no external force in the direction of increasing the rotation speed is applied, and when the water turbine 40 rotates beyond the synchronous rotation speed of the electric motor 10, This waterwheel 4
With respect to 0, the electric motor 10 acts as a load, and the overrun of the water turbine 40 and thus the compressor 1 is prevented.

Further, since the output of the electric motor 10 can be input to the compressor main body 50 through the power transmission means as described above, the amount of water stored in a dam or a reservoir as a water source is reduced, for example, in summer. Even if the output of the water turbine 40 alone is not sufficient to operate the compressor main body 50 at a desired rotation speed, this shortage is compensated for by the electric motor 1.
By supplementing with the output of 0, the compressor main body 50 can be driven at a desired rotation speed.

The shaft 44 of the water wheel 40 and the electric motor 1
The clutch means for connecting the zero rotation shaft 11 may be an electric clutch instead of the centrifugal clutch 62.

In this case, detection means RS1 for detecting the rotation speed of the turbine is provided. When the rotation speed of the water turbine 40 detected by the detection means RS1 becomes, for example, the rated rotation speed of the electric motor 10, The shaft 44 of the motor 40 and the rotating shaft 11 of the electric motor 10 are connected.

Assuming that the rated rotation speed of the electric motor 10 is 1,740 min ^-1 , for example, when the rotation speed of the water turbine 40 reaches 1,740 min ^-1 which is the rated rotation speed of the electric motor 10,
An electromagnetic clutch connects the shaft 44 of the water wheel 40 and the rotating shaft 11 of the electric motor 10 according to a detection signal of the detecting means RS1 which has detected the rotation speed of the water wheel 40, and the output of the water wheel 40 is transmitted via the electric motor 10 and the power transmission means 60. Is input to the compressor body 50.

Therefore, by connecting the shaft 44 of the water turbine 40 and the rotating shaft 11 of the electric motor 10, the load generated by the compressor main body 50 is shared by the water turbine 40 and the load on the electric motor 10 is reduced, and the power consumption of the electric motor 10 is reduced. Can be reduced.

As described above, the water turbine 40 is controlled by the electromagnetic clutch.
By immediately connecting the shaft 44 of the water turbine 40 and the rotating shaft 11 of the electric motor 10 when the rotational speed of the electric motor 10 reaches the rated rotational speed of the electric motor 10, the centrifugal clutch 62 in the above-described embodiment is compared with the case where the shaft is connected by the centrifugal clutch 62. Thus, the load on the electric motor 10 can be reduced. That is, the water wheel 40
When the rotation speed of the turbine 10 is equal to or less than the rated rotation speed of the electric motor 10 and the water wheel 40 is connected to the electric motor 10 that rotates at the rated rotation speed, the electric motor 10 tries to increase the rotation of the water wheel 40 to the rated rotation speed of the electric motor 10. For the water wheel 40
Acts as a load for zero. Therefore, in the case of the centrifugal clutch 62 in which the contact between the lining and the drum is started before the water turbine 40 reaches the rated rotation speed of the electric motor 10 as in the above-described centrifugal clutch 62, the rotation speed of the water turbine 40 Until the rotation speed is reached, the output of the electric motor 10 is consumed extra. However, when an electromagnetic clutch is used to connect the water turbine 40 to the rated rotation speed of the electric motor 10 when the rotation speed of the water turbine 40 reaches the rated rotation speed as described above, it is possible to prevent an extra load on the electric motor 10 from being applied. be able to. The centrifugal clutch 62
The electromagnetic clutch with a shorter sliding time of the sliding part compared to
Wear and deterioration due to friction are unlikely to occur, and labor for repair and replacement is reduced.

Next, another embodiment of the present invention will be described with reference to FIG.

FIG. 2 shows a water turbine driven compressor 1 according to the present invention.
1 replaces the electric motor 10 arranged in series between the water turbine 40 and the power transmission means 60 in the embodiment of FIG.
In order to enable the electric motor 10 to be connected in parallel with the water turbine 40 in this embodiment, the first speed increasing device 64 constituting the power transmission means 60 in the present embodiment.
Are provided with two input shafts 64a and 64b.
4a is connected to the shaft 44 of the water wheel 40 via the clutch means 62, and the other input shaft 64b is connected to the rotating shaft 11 of the electric motor 10 via a shaft coupling.

The two input shafts 64 of the first speed increasing device 64
a, 64b is supplied to the first speed increasing device 6
The first speed increasing device 6 via a gear mechanism 65 provided in the
4 is output to the output shaft 64 c of the first speed increasing device 64. The output is transmitted to the output shaft 64 c of the first speed increasing device 64. These two input shafts 64a, 6
The gear mechanism 65 that transmits the power input from the input shaft 4b to the output shaft 64c has a gear ratio that increases the power at the same magnification when input from the two input shafts 64a and 64b.

The other structure of the compressor 1 is the same as that of the embodiment shown in FIG.

In the water turbine driven compressor 1 configured as described above, the compressor 1 is started by the electric motor 10 as in the embodiment shown in FIG.

When the compressor 1 is started by the electric motor 10, the water turbine 4 is driven through the gear mechanism 65 in the first speed increasing device 64.
The input shaft 64a on the 0 side is also rotated.
The number of rotations of the
The output of the electric motor 10 is all transmitted to the compressor main body 50 because it has not risen enough to connect the motor and the rotating shaft 11 of the electric motor 10.

When the compressor 1 is started by the electric motor 10,
Since the rotation speed of the motor 10 is relatively fast, the compressor body 50 increases the rotation speed to the rated rotation speed of the motor in a relatively short time. Thereafter, when the rotation speed of the water turbine 40, whose rise in rotation speed is relatively slow, rises to the rated rotation speed of the electric motor 10 behind the electric motor 10, a clutch means provided between the shaft 44 of the water turbine 40 and the first speed increasing device 64 is provided. 6
2 is operated and the output of the water wheel 40 is input to the first speed increasing device. In this state, the load on the electric motor 10 is reduced, and the power consumption by the electric motor 10 is also reduced.

When the power consumption of the compressor body 50 increases and the load on the water turbine 40 and the electric motor 10 increases, the rotational speed of the compressor 1 tends to decrease due to the increase in the load. However, the motor 10 replenishes power until the operation of the electric valve MV for adjusting the amount of water introduced into the water turbine 40 in response to the increase in the load is completed, and the rotational speed of the compressor 1 is excessively reduced. Is prevented.

On the other hand, when the power consumed by the compressor main body 50 is reduced and the load on the water turbine 40 and the electric motor 10 is reduced, the electric motor 10 acts as a load on the water turbine 40, and the water turbine rotates the synchronous rotation of the electric motor 10. The rotation is suppressed from increasing more than a certain number.

[0075]

According to the above-described structure, it is possible to start up to the rated speed in a relatively short time at the time of starting, and to perform compression in a relatively short time during operation by following a change in power consumption of the compressor body. The operation method of the water turbine drive type compressor capable of changing the power input to the compressor main body and therefore stably operating the compressor main body always at a predetermined rotation speed and implementing the operation method To provide a water turbine driven compressor.

[Brief description of the drawings]

FIG. 1 is an explanatory view showing the overall configuration of a water turbine driven compressor according to the present invention.

FIG. 2 is an illustration without illustrating another embodiment of the present invention.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 compressor (turbine driven compressor) 10 electric motor 11 rotating shaft (of motor) 11a, 11b end of rotating shaft 40 water wheel 42 impeller 44 shaft (of water wheel) 46 water wheel room 46a inlet (of water wheel room) 46b Discharge port (in the water turbine room) 50 Compressor body 51 Input shaft 52 Intake port 53 Suction valve 54 Air filter 55 Discharge port 56 Lubrication port 57 Drain port 58 Coolant introduction port 59 Drain port 60 Power transmission means 62 Clutch means ( Centrifugal clutch) 64 First speed increasing device 64a, 64b Input shaft (of first speed increasing device) 64c Output shaft (of first speed increasing device) 66 Second speed increasing device 67 Oil reservoir 68 Shaft coupling 72 Discharge pipe 73 Release Pneumatic valve 74 Hydraulic cylinder 74a Primary chamber (of hydraulic cylinder) 74b Secondary chamber (of hydraulic cylinder) 81, 82, 83, 84, 85 Piping (circulation circuit of lubricating oil) 86, 87, 88 Piping (Circulation medium circulation circuit) 90 Hydraulic pump 92 Oil cooler 93 Aftercooler 96 Ventilation fan

Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat II (reference) H02K 7/18 F04B 17/00 BF term (reference) 3H069 AA05 BB04 CC02 CC03 DD12 EE14 EE32 3H073 AA07 AA27 BB02 CC12 CD12 CD18 CE07 CE26 3H074 AA10 AA16 BB19 CC11 CC50 5H607 AA00 BB01 BB04 BB06 BB07 BB26 CC03 CC05 DD03 DD19 EE02 EE04 EE24 FF07 FF27

Claims (5)

[Claims] 1. A turbine drive type compressor having a compressor main body and a water turbine driving the compressor main body, wherein an electric motor is connected to an input side of the compressor main body and the water turbine is connected via a clutch means. Then, the output of the electric motor and the output of the turbine are combined and input to the compressor body is enabled.When the rotation speed of the turbine is equal to or higher than a predetermined rotation speed set in advance, the clutch is connected via the clutch means. An operation method of a water turbine driven compressor, wherein an output of a water turbine is input to a compressor body. 2. The operation of the water turbine driven compressor according to claim 1, wherein the output of the water turbine is input to the compressor body when the rotation speed of the water turbine is equal to or higher than the rated rotation speed of the electric motor. Method. 3. A water turbine drive type compressor having a compressor main body and a water turbine driving the compressor main body, wherein an electric motor is connected to an input side of the compressor main body, and the water turbine is connected via clutch means. The clutch unit combines the output of the electric motor and the output of the water turbine so that the output can be input to the compressor main body. The clutch unit is configured to rotate the water turbine when the rotation speed of the water turbine is equal to or higher than a predetermined rotation speed. And an input side of the compressor body. 4. The motor according to claim 1, wherein one end of a rotating shaft of the electric motor is connected to a water turbine through the clutch means, and the other end of the rotating shaft of the electric motor is connected to an input side of the compressor body. The hydraulic turbine driven compressor according to claim 3. 5. An input shaft of the compressor main body is provided with two input shafts, and the electric motor is connected to one of the input shafts, and the water wheel is connected to the other of the input shafts via the clutch means. The water turbine drive type compressor according to claim 3, wherein