JP2002340278A - Pulsation damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pulsation damping device capable of damping pulsation in a pipe for carrying a fluid to normally operate an apparatus. SOLUTION: A resonance tank 5 is provided in series with an expansion tank 6 in the upstream of a pipe 102 connected to a micro-gas turbine 103. Thus, pulsation caused by intermittent gas intake of a gas compressor 104 can be damped by the expansion tank 6 and the resonance tank 5 when it is transmitted to the upstream.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pulsation damping device for damping pulsation in a pipe for transporting a fluid.

[0002]

2. Description of the Related Art In recent years, interest in energy conservation has increased,
Cogeneration tends to be introduced in office buildings. Cogeneration is a conventional power generation system that uses an engine or a turbine to recover more than 50% of primary energy that has been discarded into the atmosphere or into cooling water as heat using an exhaust heat recovery device, and to use heat for heating, cooling, hot water, etc. And a system that generates two or more secondary energies from one energy. In this system, for example, as shown in FIG. 16, a gas input from a gas meter 101 to a pipe 102 is converted into heat energy in a micro gas turbine 103. A gas compressor 104 is used in the micro gas turbine 103 shown in FIG.

However, when the gas compressor 104 of the micro gas turbine 103 is of a reciprocating type or the like, the gas intake is intermittently performed, so that a pressure fluctuation occurs in the pipe 102 according to the operation. Due to this pressure fluctuation, at the pressure measurement position P6 of the pipe 102 shown in FIG. 16, a pulsation is periodically generated as shown in FIG. 17, and the pulsation width is about 5.3 k.
Pa. Such a pulsation with a large pulsation width
Propagation to the upstream of the pipe 102 may adversely affect the operation of equipment and the combustion of other gas equipment, such as deterioration of the measurement accuracy of the gas meter 101 disposed upstream or reduction of durability. In order to attenuate the pulsation of the pipe 102, for example, a pulsation damping device 100 shown in FIG. 18 has been proposed.

The pulsation damping device 100 shown in FIG.
2 is provided with an orifice 105. And the pipe 10
2, a bypass line 106 is provided, and an electromagnetic valve 107 and an expansion tank 108 are provided in parallel with the orifice 105. The pulsation damping device 100 transmits the gas from the gas meter 101 while the solenoid valve 107 is closed to the orifice 10.
5, the gas compressor 104 of the micro gas turbine 103 is supplied to the gas compressor 104 of the micro gas turbine 103, and at time t1 in FIG. 19, the gas compressor 104 of the micro gas turbine 103 is started. At this time, at the downstream pressure measurement position P7 of the pipe 102, the gas pressure sharply decreases and pulsation occurs along with the gas suction of the gas compressor 104 of the micro gas turbine 103. The pulsation propagates upstream and is attenuated when branching to the pipe 102 and the bypass line 106. Then, the pulsation propagated to the pipe 102 is absorbed by the orifice 105 of the pipe 102 and further attenuated. On the other hand, the pulsation that has propagated to the bypass line 106 is
It is closed by the solenoid valve 107 and does not propagate to the pipe 102.

[0005] Then, the solenoid valve 107 is opened to supply gas mainly to the gas compressor 104 of the micro gas turbine 103 from the bypass line 106. When the combustion is started, at time t2 in FIG.
Gas compressor 104 of micro gas turbine 103
Start rated operation. At this time, pulsation occurs due to intermittent gas intake of the gas compressor 104 of the micro gas turbine 103, and the pulsation width gradually increases as the power generation load increases. This pulsation propagates upstream,
It is attenuated when branching to the pipe 102 and the bypass line 106. Then, the pulsation propagated to the pipe 102 is absorbed by the orifice 105 and attenuated, so that it is difficult for the pulsation to propagate upstream of the pipe 102. On the other hand, the pulsations that have propagated to the bypass line 106 cancel each other out in the expansion tank 108 and are attenuated. Therefore, the pulsation damping device 1 of FIG.
00, the orifice 105 and the expansion tank 108
As a result, the pulsation generated at the time of startup and at the time of rated operation is attenuated and hardly propagates to the upstream of the pipe 102, so that the gas meter 101 and other devices are hardly adversely affected.

[0006]

However, FIG.
The pulsation damping device 100 has a problem in the following points. (1) That is, the pulsation pulsation width of the pulsation at the downstream pressure measurement position P7 in FIG. 18 during the rated operation of the gas compressor 104 of the micro gas turbine 103 as shown in FIG. Is about 4.0 kP
a, the upstream pressure measurement position P8 in FIG.
In FIG. 21, the pulsation width was about 1.4 kPa, as shown in FIG. As can be seen from this result, the orifice 105
The expansion tank 108 can attenuate the pulsation only to about two thirds, and the pulsation damping effect at the time of rated operation was small. Therefore, the pulsation damping device 100 in FIG. 18 cannot sufficiently solve problems such as adverse effects on other gas equipment due to pulsation, effects on durability of the gas meter 101, and measurement errors of the meter.

(2) The pulsation damping device 100 shown in FIG.
Is the gas compressor 1 of the micro gas turbine 103
When the solenoid valve 107 is closed, the solenoid valve 107 is closed.
Only two were open. At this time, since the orifice diameter of the orifice 105 provided in the pipe 102 is fixed, the gas cannot be sufficiently supplied to the gas compressor 104 of the micro gas turbine 103 depending on the gas supply pressure, the gas supply pipe diameter, and the like. In some cases, the gas pressure decreased by 10 kPa or more. In this case, the micro gas turbine 10
In some cases, the protection circuit of No. 3 was activated, and the gas compressor 104 was stopped by the operation of the protection circuit.

Accordingly, the present invention has been made to solve the above-mentioned problems, and provides a pulsation damping device capable of attenuating pulsation in a pipe for transporting a fluid and operating a device normally. The purpose is to do.

[0009]

In order to solve this problem, the invention according to claim 1 is connected to a pulsation source that generates a pressure fluctuation during operation, and attenuates a pulsation generated in a pipe due to the pressure fluctuation. The pulsation damping device is characterized in that a first buffer chamber and a second buffer chamber having a fixed volume are provided in series in a pipe. In the invention according to claim 1 having the above configuration, when the pulsation source is activated and generates a pressure fluctuation,
The pulsation caused by the pressure fluctuation propagates upstream. However, the pulsation is input to the second buffer chamber and attenuated, and the pulsation attenuated in the second buffer chamber is input to the first buffer chamber and attenuated. Therefore, the pulsation generated by the pulsation generation source is attenuated twice in the first buffer chamber and the second buffer chamber, and is difficult to propagate upstream. In addition, even if the pulsation width increases with the rise in the power generation load after the pulsation source has been rated and the gas supply has started, the pulsation is doubled in the first buffer chamber and the second buffer chamber. Because it is attenuated, it is difficult to propagate upstream. Therefore, according to the first aspect of the present invention, the pulsation in the pipe can be significantly attenuated in the first buffer chamber and the second buffer chamber, and the device can be operated normally.

The invention described in claim 2 is the invention described in claim 1, wherein the first buffer chamber is a resonance tank and the second buffer chamber is an expansion tank.
According to the second aspect of the present invention having the above configuration, in addition to the operation of the first aspect, when the pulsation generated by the pulsation source propagates upstream of the pipe, the pulsation is attenuated in the expansion tank. Attenuated in the resonance tank. Pulsations having a wide range of wavelengths are attenuated in the expansion tank of the second buffer chamber, and then pulsations of a specific wavelength are selectively attenuated in the first buffer chamber. Therefore, according to the invention described in claim 2, in addition to the effect of the invention described in claim 1, pulsation can be attenuated with a simple structure, and the entire device can be made compact.

The invention according to claim 3 is the pulsation damping device according to claim 1, wherein the first buffer chamber and the second buffer chamber are expansion tanks. According to a third aspect of the present invention having the above configuration, in addition to the effect of the first aspect, the pulsation generated by the pulsation generation source is:
When propagating upstream of the pipe, it is attenuated in each of the expansion tanks connected in series. Therefore, according to the third aspect of the invention, in addition to the effects of the first aspect, pulsation can be attenuated with a simple structure, and the entire apparatus can be made compact.

The invention described in claim 4 is the invention described in claim 2, wherein the resonance tank and the expansion tank are provided in one closed tank, and the piping is inserted through the resonance tank. A through-hole that is inserted into the expansion tank to the inside and communicates with the resonance tank is formed at a symmetrical position on the outer peripheral surface. According to a fourth aspect of the present invention having the above configuration, in addition to the function of the second aspect, the resonance tank and the expansion tank are integrally attached to the pipe. The gas supplied from the upstream leaks from the through hole and fills the resonance portion, fills the expansion tank, and is supplied to the pulsation generation source. Then, when the pulsation source generates pressure fluctuation, the pulsation accompanying the pressure fluctuation propagates upstream of the pipe,
Damped in the expansion tank. The pulsation attenuated by the expansion tank is attenuated by the resonance effect from the resonance tank via the through hole when propagating to the upstream of the pipe. Therefore, in the invention described in claim 4, in addition to the effect of the invention described in claim 2, it is not necessary to connect the resonance tank and the expansion tank with a pipe, so that the structure becomes simpler and the whole apparatus can be further made. It can be made compact and the number of assembly steps can be reduced.

The invention described in claim 5 is the invention according to any one of claims 1 to 4, wherein the pipe is a first pipe provided with a first buffer chamber, A second pipe branching from the first pipe and having a second buffer chamber, wherein a flow control valve (needle valve) is provided in the first pipe in parallel with the second buffer chamber. And The invention according to claim 5 having the above-described configuration provides, in addition to the operation of the invention according to any one of claims 1 to 4, a needle valve according to a use environment such as a fluid pressure or a pipe diameter. Set the opening arbitrarily. And when the pulsation source is activated,
Pulsation occurs in response to pressure fluctuations generated by the pressure source, and the pulsation is attenuated when branching to the first pipe and the second pipe. Then, the pulsation propagated to the first pipe is absorbed and attenuated by the needle valve, and further attenuated in the first buffer chamber. On the other hand, the pulsation input to the second pipe is
Attenuated in the second buffer chamber and further attenuated in the first buffer chamber. As described above, the pulsation generated when the pulsation source is started is absorbed by the first buffer chamber, the second buffer chamber, and the needle valve, and is difficult to propagate to the upstream of the first pipe. Therefore, in the invention described in claim 5, in addition to the effect of the invention described in any one of claims 1 to 4, the gas pressure can be adjusted to be low in accordance with the use environment, so that the gas pressure can be adjusted upstream of the needle valve. Can be made gentle to prevent malfunction of the device.

The invention described in claim 6 is the invention described in claim 5, characterized in that an electromagnetic valve is provided downstream of the needle valve. Claim 6 having the above configuration.
The invention described in (5) has the effect of the invention described in claim 5,
When the pulsation generation source performs the rated operation, the pulsation width after the rated operation becomes larger than the pulsation width at the time of startup due to an increase in the power generation load, and the needle valve may not be able to sufficiently absorb the pulsation after the rated operation. Therefore, the electromagnetic valve is closed after the rated operation of the pulsation generating source, and the pulsation after the rated operation is prevented from propagating upstream of the first pipe via the needle valve. Therefore, according to the invention described in claim 6, in addition to the effect of the invention described in claim 5, propagation of pulsation to the upstream can be more effectively prevented.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment) Next, a first embodiment of a pulsation damping device according to the present invention will be described with reference to the drawings. The pulsation damping device according to the first embodiment is the same as the pulsation damping device 10 shown in FIG.
As in the case of 0, it is disposed between the gas meter 101 and the micro gas turbine 103. Therefore, here, the same reference numerals are given to the members used in the pulsation damping device of FIG. 18, and the detailed description is omitted.

The pulsation damping device 1 shown in FIG.
1 and the micro gas turbine 103 are connected by a pipe 102, and the pipe 102 is provided with a bypass line 106. The pipe 102 has a micro gas turbine 103
The needle valve 2 and the solenoid valve 3 are connected to the bypass line 106 in order to prevent the pulsation generated by the gas suction of the gas compressor 104 from propagating upstream of the pipe 102.
Are provided between the connection positions. On the other hand, the solenoid valve 4 is provided in the bypass line 106 in order to control the input of gas flowing through the pipe 102. The solenoid valves 3 and 4 are electrically connected to a control device of the micro gas turbine 103, and the control device of the micro gas turbine 103 has a function at the time of starting and at a time of steady operation of the gas compressor 104 of the micro gas turbine 103. And solenoid valves 3 and 4
A program for switching the opening and closing of the storage is stored.

The pipe 102 has a bypass line 1
The resonance tank 5 is arranged in a bump shape upstream of the position where the electromagnetic valve 4 is connected to the solenoid valve 4.
An expansion tank 6 is disposed downstream of the tank. For this reason,
The resonance tank 5 and the expansion tank 6 are connected to the pulsation damping device 1 shown in FIG.
And a gas flow path that connects the gas meter 101 and the micro gas turbine 103 to each other.

As described above, the resonance tank 5 and the expansion tank 6
Are provided in series because the expansion tank attenuates pulsations of a wide range of wavelengths, and subsequently the resonance tank selectively attenuates pulsations of specific wavelengths. The reason why the resonance tank 5 and the expansion tank 6 are combined is that the pulsation generated by the gas intake of the gas compressor 104 of the micro gas turbine 103 is combined with the pulsation damping device shown in FIG. This is because it was found through experiments that the damping can be significantly reduced. Hereinafter, the experimental method and the experimental result will be described.

In the experiment, as shown in FIG. 2, a first buffer chamber 11 was connected to a pipe 10 connected to a micro gas turbine 103.
And the second buffer chamber 12 are provided in series, and the first buffer chamber 11 and the second
An experimental pulsation damping device in which the resonance tank 5 or the expansion tank 6 was disposed in the buffer chamber 12 was used. Here, in the experiment, as the resonance tank 5, the resonance pipes 1 were installed in the closed tanks 13 and 14.
What connected 5 and 16 is used. That is, the closed tanks 13 and 14 have a diameter of 280 mm and a height of 200 mm.
It has a cylindrical shape of mm and an inner volume of 12.5 liters. And the sealed tanks 13 and 14
Means that the ends of the 200 mm long resonance tubes 15 are 50
It is connected in the state inserted by mm. One end of a resonance tube 16 having a length of 160 mm is connected to the closed tank 14, and the other end of the resonance tube 16 is connected to the pipe 10. For this reason, the closed tanks 13 and 14 are
It communicates with the pipe 10 via 5 and 16. On the other hand, the expansion tank 6 uses a 25-liter closed tank 17 partitioned in half by a partition plate 18 to provide 12.5-liter expansion chambers 17A and 17B. Partition plate 1
8, a through hole 18a is formed, and expansion chambers 17A, 17A are formed.
B is in communication. Therefore, regardless of whether the resonance tank 5 or the expansion tank 6 is provided in the first buffer chamber 11 and the second buffer chamber 12, the gas supplied from the upstream is supplied to the first buffer chamber 11 or the second buffer chamber 12.
And the micro gas turbine 10 via the second buffer chamber 12
3 is supplied to the gas compressor 104.

Then, the tank configuration of the first and second buffer chambers 11 and 12 of the experimental pulsation damping device is changed, and the gas is supplied from the upstream to the upstream of the resonance tank 5 (hereinafter, referred to as the following) according to the tank configuration. The pressure fluctuation was measured for P3. The results are shown in FIGS.

When gas is supplied to the experimental pulsation damping device and the gas compressor 104 of the micro gas turbine 103 intermittently performs gas suction, pulsation occurs in the pipe 10.
At this time, when the first buffer chamber 11 is the resonance tank 5 and the second buffer chamber 12 is the expansion tank 6, the pulsation width is about 0.5 kPa as shown in FIG. This was about one third of the pulsation width (1.4 kPa) of the device.
When both the first buffer chamber 11 and the second buffer chamber 12 are the expansion tank 6, the pulsation width is about 0.7 kPa as shown in FIG. 4, and the pulsation of the pulsation damping device shown in FIG. It became about half of the width (1.4 kPa). Furthermore, the first
When both the buffer chamber 11 and the second buffer chamber 12 are the resonance tank 5, the pulsation width is at most about 0.8 kPa as shown in FIG. 5, and the pulsation width of the pulsation damping device shown in FIG. (1.4 kPa). Accordingly, the resonance tank 5 is provided in the first buffer chamber 11, and the expansion tank 6 is provided in the second buffer chamber 12.
It has been found that the pulsation can be attenuated most when is configured.

Therefore, the resonance tank 5,
The gas compressor 104 of the micro gas turbine 103 is operated by using the experimental pulsation damping device in which the expansion tank 6 is disposed in the second buffer chamber 12 and the micro gas turbine 1 is operated.
03 (hereinafter referred to as “downstream pressure measurement position”), intermediate pressure measurement position P2 (hereinafter referred to as “intermediate pressure measurement position”), and upstream P3 of resonance tank 5.
Were measured for pressure fluctuations. The results are shown in FIGS.

When the gas compressor 104 of the micro gas turbine 103 is started, the micro gas turbine 1
A pulsation is generated due to the intermittent gas intake of the gas compressor 104 of 03, and the pulsation propagates upstream of the pipe 10. At this time, at the downstream pressure measurement position P1, as shown in FIG. 6, the pressure was reduced to about -3.2 kPa, and was pulsating with a pulsation width of about 4.0 kPa. At the intermediate pressure measurement position P2, as shown in FIG.
And then pulsated with a pulsation width of about 0.5 kPa. Further, at the upstream pressure measurement position P3, FIG.
As shown in the figure, the pressure decreased to about 1.6 kPa, and pulsation occurred at a pulsation width of about 0.3 kPa.

Therefore, the pulsation generated when the gas compressor 104 of the micro gas turbine 103 is started has a pulsation width of about 4.0 kPa to about 0.4 kPa in the expansion tank 6.
It is reduced to 5 kPa and attenuated to about 1/8. And
The pulsation attenuated in the expansion tank 6 is attenuated to about three fifths in the resonance tank 5 with the pulsation width reduced from about 0.5 kPa to about 0.3 kPa. Therefore, the pulsation width of the pulsation generated near the gas compressor 104 of the micro gas turbine 103 is attenuated to about 1/13 by passing through the expansion tank 6 and the resonance tank 5, and the pulsation of FIG. It was found that the pulsation damping effect was greater than that of the damping device 100. Therefore, the experimental pulsation damping device in which the resonance tank 5 and the expansion tank 6 are arranged in series,
The pulsation damping device 100 of FIG. 18 provided with an orifice 105
As compared with the above, pulsation and a decrease in gas pressure caused by the activation of the gas compressor 104 of the micro gas turbine 103 can be significantly reduced.

After the rated operation of the gas compressor 104 of the micro gas turbine 103 is started and the supply of gas is started, the pulsation gradually increases as the power generation load increases, and the pulsation propagates upstream. At this time, at the downstream pressure measurement position P1, as shown in FIG.
It was pulsating with the pulsation width. Also, the intermediate pressure measurement position P2
In this case, as shown in FIG. 10, pulsation occurred at a pulsation width of about 0.5 kPa. Further, at the upstream pressure measurement position P3, as shown in FIG. 11, the pulse pulsated with a pulsation width of about 0.3 kPa.

Therefore, the pulsation generated by the rated operation of the gas compressor 104 of the micro gas turbine 103 reduces the pulsation width in the expansion tank 6 from about 4.0 kPa to about 0.5 kPa, and attenuates to about 1/10. Was done. Further, the pulsation attenuated in the expansion tank 6 is reduced in the resonance tank 5 by a pulsation width of about 0.5 kPa to about 0.3 kPa.
It was attenuated to kPa and about 3/5. Therefore,
In the pulsation damping device 100 shown in FIG. 18, the pulsation at the downstream pressure measurement position P8 could be attenuated only to about two thirds at the upstream pressure measurement position P9.
And the expansion tank 6 are arranged in series, the pulsation at the downstream pressure measurement position P3 is attenuated to about 1/13 at the upstream pressure measurement position P1, and the resonance tank 5 expands. It has been found that the experimental pulsation damping device in which the tanks 6 are arranged in series has an extremely large pulsation damping effect as compared with the pulsation damping device 100 of FIG.

As is clear from the above experimental results, when the resonance tank 5 and the expansion tank 6 are arranged in series, an excellent pulsation damping effect can be obtained. Therefore, the pulsation damping device 1 of FIG. 1 employs a configuration in which the resonance tank 5 and the expansion tank 6 are arranged in series. The pulsation damping device 1 of FIG. 1 including the needle valve 2 and the like in addition to the resonance tank 5 and the expansion tank 6 operates as follows.

First, the degree of opening of the needle valve 2 is adjusted according to the diameter of the pipe 102, the amount of gas supplied, and the like, and gas is supplied from the gas meter 101 with the solenoid valves 3 and 4 closed. Then, only the solenoid valve 3 is opened, and the gas whose flow rate has been adjusted by the needle valve 2 is supplied to the gas compressor 104 of the micro gas turbine 103. The control device starts the gas compressor 104 of the micro gas turbine 103 after the time t1 in FIG. 19 from the operation of the micro gas turbine 103. At this time, since the gas compressor 104 of the micro gas turbine 103 intermittently performs gas intake, the gas compressor 1 of the micro gas turbine 103
Although the gas pressure in the vicinity of 04 sharply decreases, since the opening of the needle valve 2 is adjusted low with respect to the diameter of the pipe 102, the gas supply amount, and the like, the change upstream of the needle valve 2 is gradual. Is done.

When the gas compressor 104 of the micro gas turbine 103 performs intermittent gas intake, a pulsation is generated along with the intermittent gas intake, and tends to propagate upstream of the pipe 102. However, since the pulsation propagates by branching to the pipe 102 and the bypass line 106, the pulsation propagated to the pipe 102 and the bypass line 106 is attenuated as compared with the pulsation before the branch. Then, the pulsation propagated to the pipe 102 propagates from the electromagnetic valve 3 to the needle valve 2, but when the needle valve 2 passes through the needle valve 2 because the opening degree of the needle valve 2 is set smaller than the diameter of the pipe 102. Attenuated,
Propagated upstream. On the other hand, the pulsation input to the bypass line 106 propagates upstream through the expansion tank 6, but does not propagate upstream from the electromagnetic valve 4 because the electromagnetic valve 4 is in the closed state.

Then, at time t2 in FIG. 19 after the operation of the micro gas turbine 103, the control device outputs an electric signal to change the solenoid valve 3 from the open state to the closed state while opening the solenoid valve 4 from the closed state. Let it be in a state. Thus, the gas is supplied to the gas compressor 104 of the micro gas turbine 103 only through the bypass line 106.

Then, when the rated operation of the gas compressor 104 of the micro gas turbine 103 is started, the gas compressor 104 of the micro gas turbine 103 is intermittently sucked into the gas compressor 104 so that the gas compressor 104 of the micro gas turbine 103 has a pressure of about 4 kPa. A pulsation having a pulsation width occurs. This pulsation propagates upstream and is attenuated when branching into the pipe 102 and the bypass line 106. Here, the pulsation that has propagated to the pipe 102 is prevented from propagating upstream by the solenoid valve 3 in the closed state, so that the pulsation that has propagated to the bypass line 106 is attenuated in the same manner as in the experimental pulsation damping device. . That is, the pulsation propagated to the bypass line 106 is input to the expansion tank 6. In the expansion tank 6 having a constant volume, the gas pressure is smaller than that of the bypass line 106, so that the pulsations cancel each other and are attenuated. Therefore, the pulsation output from the expansion tank 6 has a pulsation width of about 0.5 kPa, and is attenuated to about 1/8 compared to the pulsation near the gas compressor 104 of the micro gas turbine 103. The pulsation attenuated in the expansion tank 6 is transmitted through the solenoid valve 4 to the pipe 1.
02, and is attenuated by the resonance effect from the resonance tank 5 at the connection between the resonance pipe 16 and the pipe 102.
As a result, the pulsation that has passed through the resonance tank 5 has a pulsation width of about 0.3 kPa, is attenuated to about ５ of the pulsation that has passed through the expansion tank 6, and is propagated upstream of the pipe 102. Therefore, the pulsation near the gas compressor 104 of the micro gas turbine 103 is attenuated to about 1/13 by passing through the expansion tank 6 and the resonance tank 5.

Therefore, according to the pulsation damping device 1 of FIG.
Gas compressor 104 of micro gas turbine 103
Since the pulsation generated by the rated operation passes through the expansion tank 6 and the resonance tank 5 and becomes only 0.3 kPa, the accuracy of the gas meter 101 is deteriorated and the durability of the gas meter 101 is reduced. No adverse effects. According to the pulsation damping device 1 of FIG. 1, the electromagnetic valve 3 is closed during the rated operation of the gas compressor 104 of the micro gas turbine 103, and thus the pulsation generated by the rated operation of the gas compressor 104 of the micro gas turbine 103. Can be prevented from propagating upstream of the pipe 102 via the needle valve 2.

According to the pulsation damping device 1 of FIG. 1, the pulsation caused by the activation of the gas compressor 104 of the micro gas turbine 103 is damped by the bypass line 106 and the needle valve 2 and bypassed by the solenoid valve 4. Since it is prevented from propagating to the pipe 102 via the line 106, it is difficult to propagate to the upstream of the pipe 102, which adversely affects the operation of the device, such as deteriorating the measurement accuracy of the gas meter 101 and decreasing the durability. Nothing. In addition, according to the pulsation damping device 1 of FIG. 1, the opening of the needle valve 2 is optimally adjusted with respect to the diameter of the pipe 102, the gas supply amount, and the like, so that the gas compressor 104 of the micro gas turbine 103 can be started. Due to the accompanying abnormal decrease in gas pressure, the protection circuit and the like work, and the micro gas turbine 10
3 does not stop.

(Second Embodiment) Next, a pulsation damping device according to a second embodiment of the present invention will be described with reference to FIGS. The pulsation damping device 20 of the second embodiment shown in FIG. 12 is obtained by omitting the bypass line 106, the needle valve 2, and the solenoid valves 3 and 4 of the pulsation damping device 1 of FIG. Therefore, here, the differences from the pulsation damping device 1 of FIG. 1 will be described in detail, and members common to those of the pulsation damping device 1 of FIG. 1 will be denoted by the same reference numerals and description thereof will be omitted.

In the pulsation damping device 20 shown in FIG. 12, a gas meter 101 and a micro gas turbine 103 are connected by a pipe 21. The resonance tank 5 and the expansion tank 6 are arranged in series in the pipe 21. And the gas meter 101
From the gas compressor 1 of the micro gas turbine 103
Gas is supplied to the micro gas turbine 103 after the time t1 in FIG.
Of the gas compressor 104 is started to perform gas suction.
At this time, since the expansion tank 6 and the resonance tank 5 are filled with gas, even if the gas compressor 104 of the micro gas turbine 103 performs gas suction, the gas pressure does not drop abnormally. Further, even if pulsation occurs due to intermittent gas intake of the gas compressor 104 of the micro gas turbine 103, the pulsation is attenuated by the expansion tank 6 and the resonance tank 5, and is propagated upstream of the pipe 21. Hateful.

When the gas compressor 104 of the micro gas turbine 103 starts rated operation, at a downstream pressure measurement position P4 near the gas compressor 104 of the micro gas turbine 103, as shown in FIG. Pulsation occurs. This pulsation is attenuated in the expansion tank 6 and the resonance tank 5, and the upstream pressure measurement position P5 between the resonance tank 5 and the division valve 22 is set.
Then, as shown in FIG. 14, the pulsation has a pulsation width of about 0.3 kPa. Here, since the pipe 102 is provided linearly, pressure loss in the pipe 21 can be reduced.

Therefore, according to the pulsation damping device of FIG.
If the resonance tank 5 and the expansion tank 6 are provided in series in the pipe 21, the pressure drop in the vicinity of the gas compressor 104 of the micro gas turbine 103 can be reduced by about 1.10 without providing the orifice 105 as in the pulsation damping device of FIG. 0 kPa
And the stop of the gas compressor 104 can be prevented. According to the pulsation damping device of FIG. 12, the orifice 1 provided in the pulsation damping device of FIG.
Since the structure can be simplified by omitting the bypass line 05, the bypass line 106, and the solenoid valve 107, the whole apparatus can be made compact and the cost can be reduced. Further, according to the pulsation damping device of FIG. 12, since the expansion tank 6 and the resonance tank 5 have a constant volume and adjust the gas pressure flowing through the pipe 102, the pulsation damping device of FIG. There is no need to provide the solenoid valves 107, 3 and 4, and the cost can be reduced by omitting electric wiring work when installing the tank, and the entire device can be made compact.

(Third Embodiment) Next, a third embodiment of the pulsation damping device of the present invention will be described with reference to FIG. The pulsation damping device according to the third embodiment shown in FIG. 15 has a closed tank 31 provided in a pipe 102 instead of the resonance tank 5 and the expansion tank 6 of the pulsation damping device according to the second embodiment shown in FIG. It is. Therefore, here, FIG.
The differences from the pulsation damping device of the second embodiment shown in FIG. 2 will be described in detail, and members common to the pulsation damping device of the second embodiment shown in FIG. I do.

The pulsation damping device shown in FIG.
Has a resonance tank 32 having a capacity of 17 liters and an expansion tank 33 having a capacity of 34 liters, and has a diameter of 280 m.
m, a cylindrical shape with a length of 540 mm. In the expansion tank 33, a pipe 102A inserted into the resonance tank 32 and inserted up to 280 mm into the expansion tank and a pipe 102B connected to the gas compressor 104 of the micro gas turbine 103 are coaxially connected. In the pipe 102A, through holes 36 and 37 are formed at a symmetrical position with a diameter of 23 mm.

In the closed tank 31, the gas flowing through the pipe 102 leaks from the through holes 36 and 37, and
And the expansion tank 33,
02B. And the micro gas turbine 1
When the gas intake starts by the activation of the gas compressor 104 in FIG.
Since the gas that fills the gas is sucked, abnormal lowering of the gas pressure is prevented. In addition, pulsations generated when the gas compressor 104 of the micro gas turbine 103 is started or during rated operation are input from the pipe 102B to the expansion tank 33, are canceled each other, are attenuated, and are input to the pipe 102A. The pulsation propagating through the pipe 102A is generated by the through-hole 3
The signal is attenuated by the resonance effect from the resonance section 32 through the elements 6 and 37. Therefore, the pulsation generated when the gas compressor 104 of the micro gas turbine 103 is started or when the rated operation is performed is greatly attenuated in the closed tank 31 and propagated upstream. Therefore, the pulsation damping device of FIG.
It is not necessary to connect the resonance tank 5 and the expansion tank 5 with piping as in the pulsation damping device of the second embodiment shown in FIG. it can.

It should be noted that the present invention is not limited to the above embodiment, and various changes can be made without departing from the gist of the present invention. (1) The dimensions, tank capacity, and the like of the components described in the first to third embodiments are not limited to the above-described embodiments, and can be appropriately changed according to the use environment. For example, without changing the capacity of the resonance tank 5, the expansion tank 6, and the closed tank 31,
The diameter may be increased and the height may be reduced. (2) In the first to third embodiments, the resonance tank is provided in the first buffer chamber and the expansion tank is provided in the second buffer chamber. However, the expansion tank is provided in the first buffer chamber, and the resonance tank is provided in the second buffer chamber. May be provided. (3) In the first embodiment and the second embodiment, 2
An expansion tank 6 having two closed tanks connected in series and a resonance tank having two closed tanks connected by a resonance pipe 15 were used. However, an expansion tank without partitions, a branch pipe type resonance chamber or the like in the pipe 102 was provided. May be. (4) In the first embodiment, the resonance tank 5 and the expansion tank 6 are combined and disposed in the pulsation damping device 1. However, as shown in FIG. 22, the expansion tanks 6 may be combined.

[0042]

As described above, according to the first aspect of the present invention, there is provided a pulsation damping device that is connected to a pulsation generating source that generates a pressure fluctuation during operation and attenuates a pulsation generated in a pipe due to the pressure fluctuation. Since the first buffer chamber and the second buffer chamber having a fixed volume are provided in series in the pipe, the pulsation in the pipe is largely attenuated in the first buffer chamber and the second buffer chamber, and the apparatus operates normally. Can be.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a pulsation damping device according to a first embodiment of the present invention.

FIG. 2 is a schematic configuration diagram of an experimental pulsation damping device used in a pulsation damping effect test.

FIG. 3 is a graph showing the pulsation damping effect of each tank configuration in the experimental pulsation damping device, wherein the first buffer chamber is a resonance tank and the second buffer chamber is an expansion tank at an upstream pressure measurement position P3. 9 is a graph showing the results of gas pressure pulsation measurement during rated operation of a micro gas turbine.

FIG. 4 is a graph showing the pulsation damping effect of each tank configuration in the experimental pulsation damping device, wherein the microscopic measurement is performed at the upstream pressure measurement position P3 when both the first buffer chamber and the second buffer chamber are configured as expansion tanks. 5 is a graph showing the results of gas pressure pulsation measurement during gas turbine rated operation.

FIG. 5 is also a graph showing gas pressure pulsation measurement results for each tank configuration in the experimental pulsation damping device, and shows an upstream pressure measurement position P3 when both the first buffer chamber and the second buffer chamber are configured as resonance tanks. 5 is a graph showing gas pressure pulsation measurement results during rated operation of the micro gas turbine in FIG.

FIG. 6 is a view showing a gas pressure pulsation measurement result at the time of starting a gas compressor at a downstream pressure measurement position P1 of an experimental pulsation damping device combining a resonance tank and an expansion tank.

FIG. 7 is a graph showing the results of measurement of gas pressure pulsation at the time of starting the gas compressor at the intermediate pressure measurement position P2 of the experimental pulsation damping device combining the resonance tank and the expansion tank.

FIG. 8 is a view showing the results of gas pressure pulsation measurement at the time of starting the gas compressor at the upstream pressure measurement position P3 of the experimental pulsation damping device combining the resonance tank and the expansion tank.

FIG. 9 is a diagram showing the results of gas pressure pulsation measurement at the time of rated operation of the micro gas turbine at the downstream pressure measurement position P1 of the experimental pulsation damping device combining the resonance tank and the expansion tank.

FIG. 10 is a graph showing the results of gas pressure pulsation measurement at the time of rated operation of the micro gas turbine at the intermediate pressure measurement position P2 of the experimental pulsation damping device combining the resonance tank and the expansion tank.

FIG. 11 is a view showing a gas pressure pulsation measurement result at the time of rated operation of the micro gas turbine at the upstream pressure measurement position P3 of the experimental pulsation damping device combining the resonance tank and the expansion tank.

FIG. 12 is a schematic configuration diagram of a pulsation damping device according to a second embodiment of the present invention.

FIG. 13 is a view showing a gas pressure pulsation measurement result at the downstream pressure measurement position P4 of the pulsation damping device of FIG. 12 during rated operation of the micro gas turbine.

FIG. 14 is a graph showing the results of gas pressure pulsation measurement at the micro gas turbine upstream pressure measurement position P5 during rated operation of the pulsation damping device of FIG. 12;

FIG. 15 is a schematic configuration diagram of a pulsation damping device according to a third embodiment of the present invention.

FIG. 16 is a schematic diagram of a connection structure between a micro gas turbine and a gas meter.

FIG. 17 is a view showing a gas pressure pulsation measurement result at the time of rated operation of the micro gas turbine at the pressure measurement position P6 in FIG. 16;

FIG. 18 is a schematic view of a conventional pulsation damping device.

FIG. 19 is a diagram showing pressure fluctuations from the start of the micro gas turbine to the rated output at the pressure measurement position P6 in FIG.

FIG. 20 is a view showing a gas pressure pulsation measurement result at the time of rated operation of the micro gas turbine at the downstream pressure measurement position P7 in FIG. 18;

FIG. 21 is a diagram showing a gas pressure pulsation measurement result at the time of rated operation of the micro gas turbine at the upstream pressure measurement position P8 in FIG. 18;

FIG. 22 is a diagram showing a modified example of the pulsation damping device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Pulsation damping device 2 Needle valve 3,4,107 Solenoid valve 5,32 Resonance tank 6,33 Expansion tank 31 Sealed tank 36,37 Through hole 101 Gas meter 102,102A, 102B Piping 103 Micro gas turbine 104 Gas compressor 105 Orifice 106 Bypass line

Continuation of front page (72) Inventor Yoshiharu Ito 19-18 Sakuradacho, Atsuta-ku, Nagoya-shi, Aichi F-term in Higashi Kunigas Co., Ltd. 3H025 CA02 CB41

Claims (6)

[Claims] 1. A pulsation damping device connected to a pulsation generating source that generates a pressure fluctuation during operation and attenuating a pulsation generated in a pipe due to the pressure fluctuation, wherein a first buffer chamber having a fixed volume in the pipe and a second buffer. A pulsation damping device characterized by providing chambers in series. 2. The pulsation damping device according to claim 1, wherein said first buffer chamber is a resonance tank, and said second buffer chamber is an expansion tank. 3. The pulsation damping device according to claim 1, wherein the first buffer chamber and the second buffer chamber are expansion tanks to which the pipes are connected on opposing side surfaces. Pulsation damping device. 4. The pulsation damping device according to claim 2, wherein the resonance tank and the expansion tank are provided in a single closed tank, and the pipe is inserted through the resonance tank so that the resonance tank is connected to the expansion tank. A pulsation damping device, wherein a through hole that is inserted to the inside and communicates with the resonance tank is formed at a symmetrical position on an outer peripheral surface. 5. The pulsation damping device according to claim 1, wherein the pipe comprises: a first pipe provided with the first buffer chamber; and the first pipe. And the second
A pulsation damping device, comprising: a second pipe provided with a buffer chamber; and a needle valve provided in the first pipe in parallel with the second buffer chamber. 6. The pulsation damping device according to claim 5, wherein an electromagnetic valve is provided downstream of the needle valve.