WO2018163419A1

WO2018163419A1 - Intake/exhaust device and natural gas treatment facility

Info

Publication number: WO2018163419A1
Application number: PCT/JP2017/009767
Authority: WO
Inventors: 松尾　知明; 謙角谷; 瑞穂小巻
Original assignee: 日揮株式会社
Priority date: 2017-03-10
Filing date: 2017-03-10
Publication date: 2018-09-13
Also published as: JPWO2018163419A1

Abstract

The purpose of the present invention is to provide an intake/exhaust device capable of cooling intake air of a gas turbine by using exhaust gas of the gas turbine and having a simple configuration. [Problem] Provided is an intake/exhaust device for supplying and discharging air to and from a gas turbine 2, wherein an intake part 3 supplies outside air to an air compressor, and an exhaust flow path 4 discharges exhaust gas discharged from the gas turbine 2. A thermoacoustic engine 5 is provided with, on pipelines 501, 502 containing working gas, a first stack 51 which causes the differential gas to vibrate when, relative to one end side of the first stack 51, the other end side is heated to a higher temperature, and a second stack 52 disposed on the downstream side in the direction of propagation of the vibration and forming a low-temperature part where, relative to one end side of the second stack 52, the other end side has a lower temperature. The other end side of the first stack 51 is heated by using exhaust gas flowing in the exhaust flow path 4, and the air taken in from the intake part 3 is cooled by using the low-temperature part disposed on the other end side of the second stack 52.

Description

Intake and exhaust system and natural gas processing equipment

The present invention relates to a technique for supplying air for fuel gas combustion to a gas turbine.

NG processing equipment that liquefies natural gas (NG), separates and recovers condensate, etc. includes a refrigerant compressor that compresses the refrigerant that cools NG, and power generation that generates electricity used in the NG processing equipment. A gas turbine may be provided to drive the machine.
High-temperature exhaust gas is discharged from the gas turbine that obtains the driving force of the turbine by burning the fuel gas. Therefore, high-temperature thermal fluid such as steam and hot oil can be generated using the exhaust gas. The obtained thermal fluid is operated using various heating devices provided in the NG treatment facility (for example, regeneration of an absorbent or adsorbent for pretreatment of NG, separation of heavy liquid from NG Used for rectification).

On the other hand, the gas turbine has a characteristic that the output decreases when the temperature of the air taken into the air compressor that compresses the combustion air rises, and therefore has a system for cooling the air taken into the gas turbine. There is also.
For example, in Patent Document 1, an absorption refrigerator using ammonia or lithium bromide as an absorbing liquid and water as a refrigerant is provided for a gas turbine provided in an NG treatment facility, and cooling of the gas turbine intake air by the refrigerant is performed. And a technique for regenerating the absorbing liquid using the exhaust gas of the gas turbine.

However, the absorption chiller requires installation of a power machine such as a pump used for feeding an absorbing liquid or a refrigerant, and the apparatus configuration becomes large, so there are problems in terms of equipment cost and maintainability.
Patent Document 2 describes a technology for recovering cooling exhaust heat of a blast furnace using a thermoacoustic engine and cooling intake air of a motor-driven air compressor. However, Patent Literature 2 describes a technology for cooling gas turbine intake air. There is no.

Australian Patent Application Publication: AU20133203082A1 JP 2014-222128 A

The present invention has been made under such a background, and an object of the present invention is to cool the gas turbine intake air using the exhaust gas of the gas turbine and to have a simple configuration. Another object of the present invention is to provide a natural gas processing facility provided with the intake / exhaust device.

An intake / exhaust device of the present invention is an intake / exhaust device that cools air supplied to an air compressor provided in the gas turbine using exhaust gas exhausted from a gas turbine,
An intake section for taking in external air and supplying it to the air compressor;
An exhaust passage for exhausting exhaust gas exhausted from the gas turbine;
A stack that is an assembly of a plurality of flow paths that are narrower than the pipe line, and the other end side is heated to a higher temperature than the one end side in the pipe line in which the working gas is sealed. A first stack for generating a vibration in the gas, and provided on the downstream side in the propagation direction of the vibration generated in the first stack, along the propagation direction of the vibration. A thermoacoustic engine provided with a second stack for forming a low temperature part having a low temperature,
The other end side of the first stack is heated using the exhaust gas flowing through the discharge flow path, and the air taken into the intake portion uses the low temperature part on the other end side of the second stack. And is cooled.

The intake / exhaust device may have the following features.
(A) On the other end side of the first stack, a high-temperature heat exchanging section is provided for exchanging heat between the exhaust gas flowing through the discharge passage and the working gas in the pipe. Also, a low temperature heat exchange section for performing heat exchange between the air taken into the intake section and the low temperature section is provided on the other end side of the second stack.
(B) The exhaust passage is provided with a heating medium heating unit for heating the heating medium by heat exchange with the exhaust gas, and the heating medium heating unit is connected to the other end side of the first stack. A high-temperature heat exchange section is provided for heat exchange between the heated heating medium and the working gas in the pipe. The other end of the second stack is provided with a low temperature heat exchange unit for cooling the refrigerant by heat exchange with the low temperature unit, and the intake unit is cooled by the low temperature heat exchange unit. An air cooling unit is provided for cooling the air taken into the intake unit by heat exchange with the refrigerant.
(C) a first discharge channel that is the discharge channel related to the heating of the other end side of the first stack using the exhaust gas;
A second discharge flow path for discharging the exhaust gas without heating the other end of the first stack;
A switching mechanism that switches a discharge destination of the exhaust gas exhausted from the gas turbine between the first discharge flow path and the second discharge flow path, and the switching mechanism has an output of the gas turbine. The exhaust gas exhaust destination is set as a first exhaust flow path when the intake cooling output is equal to or higher than a preset value, and the exhaust gas exhaust destination is output when the gas turbine output is smaller than the intake cooling output. The discharge channel is switched so that is the second discharge channel. At this time, the intake cooling output is set to a value within a range of 50% or more and less than 100% of the rated output of the gas turbine.

(D) a first discharge channel that is the discharge channel related to the heating of the other end side of the first stack using the exhaust gas, and a position for heating the other end side of the first stack A second exhaust passage that is branched upstream from the first exhaust passage and provided with an exhaust heat recovery unit for heating the thermal fluid with the exhaust gas, and exhausted from the gas turbine A flow rate adjusting mechanism for adjusting a flow rate for distributing the exhaust gas into the first discharge flow channel and the second discharge flow channel.
(E) In (d), a thermal fluid flow path through which the heated thermal fluid flowing out from the exhaust heat recovery section flows, a thermal fluid temperature measurement section that measures the temperature of the thermal fluid flowing in the thermal fluid flow path, The flow rate adjustment mechanism includes a part of the exhaust gas exhausted from the gas turbine so that the temperature of the thermal fluid measured by the thermal fluid temperature measurement unit approaches a predetermined target temperature. And adjusting the flow rate to flow to the second discharge flow path, and distributing the remaining exhaust gas to the first discharge flow path.
(F) In (d), an intake air temperature measurement unit that measures the temperature of the air taken into the intake unit and cooled using the low temperature unit,
When the temperature of the cooled air measured by the intake air temperature measurement unit is lower than a preset lower limit temperature, the air flow adjusting mechanism has a temperature of the cooled air that is equal to or higher than the lower limit temperature. The exhaust gas distributed to the first discharge flow path is decreased so that the flow rate of the exhaust gas flowing through the exhaust gas to the second discharge flow path side is increased by the decrease of the first discharge flow path.
(G) The gas turbine is provided in a natural gas processing facility for liquefying natural gas or separating / recovering components in the natural gas, and compresses a natural gas processing refrigerant for cooling the natural gas. For driving.

A natural gas processing facility according to another invention compresses a natural gas processing refrigerant that cools natural gas in a natural gas processing facility that liquefies natural gas or separates and recovers components in natural gas. A refrigerant compressor, a gas turbine that drives the refrigerant compressor, and the intake and exhaust device described above are provided.

Since the present invention performs exhaust heat recovery and intake air cooling of a gas turbine using a thermoacoustic engine having a simple configuration, an exhaust heat recovery / intake air cooling mechanism that is low in cost and has good maintainability can be configured. .

It is explanatory drawing of the NG liquefaction installation provided with the gas turbine provided with the intake / exhaust device which concerns on embodiment. It is a block diagram of the gas turbine provided with the said intake / exhaust apparatus. It is a block diagram of the said intake / exhaust device. It is a block diagram of the intake / exhaust device which concerns on other embodiment. It is a 1st operation explanatory view of the change mechanism which changes the exhaust passage of exhaust gas according to the load of a gas turbine. It is 2nd operation | movement explanatory drawing of the said switching mechanism. It is a block diagram of the flow volume adjustment mechanism which distributes the discharge flow volume of exhaust gas according to the intake temperature of a gas turbine. It is a flowchart which shows the flow of the operation | movement which concerns on the said flow volume adjustment mechanism.

FIG. 1 shows a configuration example of an NG liquefaction facility (natural gas processing facility) in which a gas turbine 2 including an intake / exhaust device according to an embodiment is provided.
The NG liquefaction facility pre-cools NG from which impurities have been removed by pre-treatment with a pre-cooling heat exchanger 11 and gas-liquid separation with a scrub column 12, followed by a cryogenic main heat exchanger (MCHE). ) Liquefied at 13 and supercooled to obtain LNG. In addition, the liquid separated from the gas-liquid in the scrub column 12 is separated into light components such as propane and butane and liquid condensate at room temperature by the rectification unit 14 having a plurality of rectification columns. The component is returned to MCHE13.

The NG liquefaction facility is provided with a C3 compressor 15 that compresses the C3 refrigerant for the precooling heat exchanger 11 and an MR compressor 16 that compresses a mixed refrigerant (MR: Mixed Refrigerant) used in the MCHE 13. ing. In the following description, the C3 compressor 15 and the MR compressor 16 are collectively referred to as “refrigerant compressor 10”.

The NG liquefaction facility of this example includes a gas turbine 2 as a power source for driving the refrigerant compressor 10. As shown in FIG. 2, the gas turbine 2 is rotated by combustion of an air compressor 21 that compresses combustion air and fuel gas supplied into the compressed air, and the refrigerant compressor 10 and the air compressor 21. And a turbine 22 for obtaining a driving force.
The gas turbine 2 may be constituted by a large industrial gas turbine having a rated output of, for example, 80 MW or more, or may be constituted by a relatively small aircraft diverting gas turbine having a rated output of about 25 MW to 60 MW. .

The gas turbine 2 having the above-described configuration includes an intake section 3 for supplying air taken in from the outside to the air compressor 21, and an exhaust gas after combustion exhausted from the turbine 22 via a chimney (not shown). And a discharge channel 4 for discharging to the outside. The intake section 3 and the exhaust flow path 4 constitute the intake / exhaust device of this example.
When a plurality of gas turbines 2 are provided in the NG liquefaction facility, all of the plurality of gas turbines 2 may be provided with the intake / exhaust device of the present example, or a part of the plurality of gas turbines 2 An intake / exhaust device may be provided.

The intake section 3 includes an air intake surface in which, for example, an inclined roof-shaped hood 301 having an opening on the lower surface side is arranged in the vertical direction, and a filter for removing dust and a silencer for noise reduction (both not shown) are provided inside. It is configured as a housed intake duct 302. The downstream end of the intake duct 302 is connected to the air compressor 21 of the gas turbine 2.

A discharge passage 4 for discharging combustion exhaust gas is connected to the outlet side of the turbine 22 of the gas turbine 2. The temperature of the exhaust gas at the exit position of the turbine 22 has a high temperature of about 350 to 600 ° C. The NG liquefaction facility may be provided with a waste heat recovery unit (WHRU) that uses this exhaust gas to obtain a high-temperature thermal fluid such as steam or hot oil.

The exhaust flow path 4 of the present example branches the exhaust gas flow path connected to the outlet of the turbine 22 and flows a part of the exhaust gas to the WHRU to obtain a thermal fluid, while the remaining exhaust gas is discharged to the exhaust flow path of the present example. 4 (see, for example, FIG. 7 described later). In addition, for example, a WHRU is provided on the outlet side of the turbine 22 to heat the thermal fluid, and the exhaust gas after exhaust heat recovery whose temperature is lower than the above-described temperature of about 350 to 600 ° C. flows through the WHRU outlet. A discharge channel 4 may be provided. In addition, the entire amount of the exhaust gas may flow through the exhaust passage 4 without providing WHRU on the outlet side of the turbine 22.

When a plurality of gas turbines 2 are provided in the NG liquefaction facility, each gas turbine 2 may be provided with a discharge flow path 4 or a flow path through which exhaust gas discharged from these discharge flow paths 4 flows. And a plurality of gas turbine 2 common discharge flow paths 4 may be provided. When providing a common exhaust flow path 4 for a plurality of gas turbines 2, each intake / exhaust gas is provided by an intake section 3 provided individually for each gas turbine 2 and a common exhaust flow path 4. The device is configured.

The intake / exhaust device of the present example having the above-described configuration includes the thermoacoustic engine 5 that cools the air taken into the intake section 3 using the exhaust gas flowing in the discharge flow path 4. The thermoacoustic engine 5 uses the thermoacoustic phenomenon to convert the thermal energy of the exhaust gas flowing through the discharge passage 4 into vibration, and the vibration is converted into a pipe line (heating side loop pipe line 501-connecting pipe line 503-cooling side). After propagating in the loop pipe line 502), a low-temperature part is formed using the energy of vibration to cool the air.

More specifically, the thermoacoustic engine 5 propagates from the heating side loop conduit 501 provided with the first stack 51 that generates vibrations using the exhaust gas flowing through the discharge passage 4 and the heating side loop conduit 501 side. And a cooling-side loop conduit 502 provided with a second stack 52 that forms a low-temperature portion using the generated vibration. The heating side loop conduit 501 and the cooling side loop conduit 502 are connected via a connecting conduit 503.

The heating side loop pipe line 501, the cooling side loop pipe line 502, and the connecting pipe line 503 are each constituted by a pipe having a diameter of about several tens of centimeters to several meters, and inside thereof is operated with air, argon, helium, or the like. Gas is sealed.
For example, the heating-side loop conduit 501 is constituted by a square annular loop having a side of about several tens of centimeters to several meters, and an aggregate (stack) of channels narrower than the heating-side loop conduit 501 is formed on one side. The first stack 51 is interposed. The first stack 51 may have a structure in which narrow tubes having a diameter of, for example, several centimeters to several tens of centimeters are bundled, or a plurality of columns having the diameter described above from one end side to the other end side of the columnar member. A honeycomb structure in which the flow paths are formed may be used.

At one end of the first stack 51, one end of the first stack 51 is brought to a predetermined temperature within a range of 4 to 20 ° C., for example, by heat exchange with a temperature adjusting fluid such as constant temperature water. A constant temperature heat exchanging section 511 for maintaining is provided. When the first stack 51 in which a plurality of thin tubes are bundled is provided, the constant temperature heat exchanging unit 511 adopts a shell and tube structure in which water flows into a shell in which one end of these thin tubes is inserted. Cases can be illustrated. In addition, when the first stack 51 having the honeycomb structure is provided, an example in which a jacket structure in which the outer peripheral surface of one end of the member in which the flow path is formed is covered with a jacket through which water flows is employed is illustrated. Can do.

The temperature-adjusting water used in the constant temperature heat exchanger 511 can be general industrial water used in the factory of the NG liquefaction facility. At this time, when the required amount of industrial water can be supplied using the pressure of the industrial water header, a unique pump (power machine) for supplying industrial water to the constant temperature heat exchanger 511 is not provided. May be. In addition, the embodiment which provides the small pump which supplies industrial water to the constant temperature heat exchange part 511 as needed is not denied. In addition, even when a long-term periodic temperature change due to a seasonal change or the like occurs, the supply flow rate of industrial water is set so that the temperature at one end of the first stack 51 can be maintained at a predetermined temperature. You may provide the flow control valve etc. which increase / decrease.

Further, the other end side of the first stack 51 has an exhaust gas flowing through the discharge flow path 4 so that the temperature on the other end side is kept at a constant temperature by the constant temperature heat exchanger 511. A high temperature heat exchanging section 512 for heating to a high temperature is provided.

As a configuration of the high-temperature heat exchange unit 512, a case where a heat exchanger having a shell and tube structure is used can be exemplified. Specifically, a casing (shell) that forms the main body of the high-temperature heat exchange unit 512 is provided at a position sandwiched by the main body of the discharge flow channel 4 from the upstream side and the downstream side in the flow direction of the exhaust gas. One surface of the casing portion arranged to face the direction intersecting the direction is connected to the first stack 51, and the other surface is connected to the heating-side loop conduit 501. And, an example of disposing a large number of heat exchange thin tubes (tubes) through which exhaust gas flows so as to penetrate the inside of the housing portion from the upstream side toward the downstream side along the flow direction of the exhaust gas is illustrated. it can.

The cooling side loop pipe line 502 is constituted by a rectangular loop having a side of about several tens of centimeters to several meters, like the heating side loop pipe line 501, and a second stack 52 is interposed on one side. ing. Since the second stack 52 has substantially the same configuration as the first stack 51, detailed description thereof is omitted, but a structure in which a plurality of thin tubes are bundled or a honeycomb structure can be used.

At one end of the second stack 52, one end of the second stack 52 is placed at a predetermined temperature within a range of, for example, 4 to 20 ° C. by heat exchange with a constant temperature water such as a temperature adjusting fluid or industrial water. A constant temperature heat exchanging section 521 that keeps the temperature is provided. The configuration of the constant temperature heat exchange unit 521 and the industrial water supply mechanism are the same as the example of the constant temperature heat exchange unit 511 on the heating side loop pipe line 501 side, and thus the description thereof is omitted.

On the other end side of the second stack 52, a low temperature heat exchanging section 522 that cools the air taken into the intake section 3 by heat exchange with the low temperature section formed at the other end section is provided.
As an example of the configuration of the low-temperature heat exchange unit 522, for example, a shell-and-tube heat exchanger similar to the high-temperature heat exchange unit 512 may be provided at the inlet of the intake duct 302 that configures the intake unit 3. . In this example, the casing part forming the shell of the low-temperature heat exchange part 522 is arranged in the intake duct 302 so as to be located in the low-temperature part of the second stack 52, and along the air flow direction in the intake duct 302. A large number of thin tubes (tubes) for heat exchange penetrating the inside of the housing are provided to cool the air flowing in the narrow tubes.

The connection pipe line 503 connects the heating side loop pipe line 501 provided on the discharge flow path 4 side and the cooling side loop pipe line 502 provided on the intake section 3 side, and is generated in the first stack 51. The transmitted vibration is propagated to the cooling side loop pipe line 502.

In the thermoacoustic engine 5 having the above-described configuration, when the gas turbine 2 is operated and high-temperature exhaust gas is exhausted from the turbine 22 to the discharge passage 4, the first temperature maintained at a constant temperature by the constant temperature heat exchange unit 511. A temperature difference is generated between one end side of the stack 51 and the other end side of the first stack 51 heated by the high temperature heat exchange unit 512. At this time, vibration is generated in the working gas in the first stack 51 due to a thermoacoustic phenomenon, and this vibration is transferred from the other end of the first stack 51 to the working gas sealed in the heating-side loop conduit 501. And propagate.

A part of the propagating vibration circulates in the heating side loop pipe 501 and amplifies the energy that generates the vibration. Further, part of the vibration propagates to the cooling side loop conduit 502 side via the connection conduit 503. The vibration introduced into the cooling side loop pipe line 502 is introduced into one end side of the second stack 52 maintained at a constant temperature by the constant temperature heat exchanger 521, and in the flow path constituting the second stack 52, As the vibration propagates, the heat release and contraction of the working gas are repeated, and the temperature gradually decreases to form a low temperature portion. By providing the low temperature heat exchange part 522 in this low temperature part, the air taken in the intake part 3 can be cooled.

When the air taken into the intake section 3 is cooled by the low-temperature heat exchange section 522, the operation efficiency of the gas turbine 2 (for example, output per unit consumption amount of fuel gas) can be improved.
The vibration that has passed through the low-temperature heat exchanging section 522 merges with the vibration propagated from the connection pipe line 503 side, circulates in the cooling-side loop pipe line 502, and is introduced again into the second stack 52.

The intake / exhaust device according to the present embodiment has the following effects. As a basic configuration, it is not necessary to install a power machine, and the exhaust heat recovery of the gas turbine 2 and the intake air cooling are performed by using the thermoacoustic engine 5 with a simple configuration. An intake air cooling mechanism can be configured.

Here, FIG. 3 shows an example in which the high-temperature heat exchanging part 512 is directly incorporated in the exhaust passage 4 to recover exhaust heat, and the low-temperature heat exchanging part 522 is directly incorporated in the intake part 3 to cool the air. It was.
However, the air taken into the intake section 3 using the method of heating the other end side of the first stack 51 in the high temperature heat exchanging section 512 or the low temperature section formed on the other end side of the second stack 52. The method of cooling is not limited to the direct heat exchange illustrated in FIG.

For example, in FIG. 4, the heating medium is passed through the heating medium heating unit 41 provided in the discharge channel 4, and the heating medium whose temperature has been increased is supplied to the high temperature heat exchanging unit 512 through the heating medium channel 411. The example of the thermoacoustic engine 5a which employ | adopted the indirect system heating which heats the other end side of the 1st stack 51 is shown. Steam, hot oil, or the like is used as the heat medium.

Further, the thermoacoustic engine 5a shown in FIG. 4 causes the refrigerant to flow through the low-temperature heat exchanging unit 522, and the refrigerant whose temperature has decreased is supplied to the air cooling unit 31 provided in the intake unit 3 via the refrigerant channel 311. The example which employ | adopted indirect system cooling which cools air by supplying is shown. As the heat medium, industrial water or the like is used.
Further, as shown in FIGS. 3 and 4, it is not essential that the exhaust heat recovery from the exhaust flow path 4 and the cooling of the air taken into the intake section 3 be a direct method or an indirect method. One of the heat exchange unit 512 and the constant temperature heat exchange unit 521 may be a direct method, and the other may be an indirect method.

Next, using FIGS. 5 and 6, the

thermoacoustic engines

5 and 5 a are used with the high-temperature heat exchange unit 512 shown in FIG. 3 and the heating medium heating unit 41 shown in FIG. An embodiment in which the state in which intake air cooling is performed and the state in which the high temperature heat exchange unit 512 and the heat medium heating unit 41 are brought into an offline state and the intake air cooling is stopped will be described.

The gas turbine 2 is designed to have the highest operating efficiency when operating at the rated output. For this reason, when the load of the refrigerant compressor 10 decreases due to a decrease in the amount of NG processing in the NG liquefaction facility, the output of the gas turbine 2 decreases in accordance with the load decrease of the refrigerant compressor 10 (turn-down operation). Also, efficient operation cannot be realized.
In this state, if the air taken in from the intake section 3 is cooled using the

thermoacoustic engines

5 and 5a, the output of the gas turbine 2 is further reduced, and the operation efficiency is deteriorated.

Therefore, the intake / exhaust device shown in FIGS. 5 and 6 branches from the discharge flow path 4 at a position upstream of the high-temperature heat exchanging section 512 (or the heat medium heating section 41; hereinafter the same in the description of FIGS. The exhaust gas exhausted from the gas turbine 2 (turbine 22) is provided with a bypass flow path (second discharge flow path) 4a for discharging the exhaust gas to the outside without passing through the high-temperature heat exchange section 512. .

The exhaust passage 4 is opened when the flow of exhaust gas to the high-temperature heat exchanging section 512 side is stopped and gas is caused to flow to the thermoacoustic engine side damper 42 constituted by, for example, a guillotine damper and the bypass passage 4a side. For example, a bypass flow path side damper 43 configured by a foldable damper is provided. The thermoacoustic engine side damper 42 and the bypass flow path side damper 43 are provided with a drive mechanism (not shown), for example, from the control unit 6 constituted by a DCS (Distributed Control System) for controlling the entire NG liquefaction facility. The opening / closing operation is automatically executed based on the control signal. The thermoacoustic engine side damper 42 and the bypass flow path side damper 43 constitute a switching mechanism for switching the discharge destination of the exhaust gas exhausted from the gas turbine 2 between the discharge flow path 4 and the bypass flow path 4a described above.

Furthermore, the control unit 6 detects the output of the gas turbine 2, and the output of the gas turbine 2 is a preset output that is 50% or more and less than 100% of the rated output, more preferably 50% or more and 98% or less. In the case of the above (referred to as “intake cooling output”), the exhaust gas exhaust destination is used as the exhaust flow path 4 and control is performed to operate the

thermoacoustic engines

5 and 5a.

On the other hand, when the output of the gas turbine 2 is in a turn-down operation state where the output of the gas turbine 2 is smaller than the intake cooling output, control is performed to switch the exhaust gas exhaust destination to the bypass flow path 4a. As a result, the operation of the

thermoacoustic engines

5 and 5a is stopped, and the temperature of the air supplied to the air compressor 21 rises, thereby improving the operating efficiency of the gas turbine 2 and reducing the consumption of combustion gas. You can do that.
Further, when the exhaust gas switched to the thermoacoustic engine 5a side is returned to the thermoacoustic engine 5 in order to suppress frequent switching operation, a predetermined offset value is added to the intake air cooling output, and the gas turbine 2 The switching mechanism may be activated when the output exceeds the intake air cooling output with the offset added.

In the embodiment shown in FIGS. 5 and 6, the example in which the exhaust gas exhaust destination is automatically switched between the exhaust flow path 4 and the bypass flow path 4a based on the control signal from the control unit 6 has been described. Automatic control is not an essential requirement. For example, when the output of the gas turbine 2 is stabilized in a state where the output is equal to or lower than the intake cooling output, the operator manually operates the thermoacoustic engine side damper 42 and the bypass flow path side damper 43 to switch between the discharge flow path 4 and the bypass flow path 4a. May be performed.

Next, an embodiment in which the flow rate of the exhaust gas is distributed between the thermoacoustic engine 5 and the WHRU 46 will be described with reference to FIGS.
The intake / exhaust device shown in FIG. 7 has an exhaust heat recovery flow path (second discharge flow path) 4b branched from the discharge flow path 4 (first discharge flow path) at a position upstream of the high temperature heat exchanging section 512. Is provided. In this exhaust heat recovery flow path 4b, there is a WHRU (exhaust heat recovery unit) 46 that heats hot oil, which is a thermal fluid, using exhaust heat of exhaust gas exhausted from the gas turbine 2 (turbine 22). Is provided.

In addition, a thermoacoustic engine side flow rate adjustment damper 44 that adjusts the flow rate of the exhaust gas flowing to the discharge flow channel 4 side is provided at a position downstream of the high temperature heat exchanging part 512 of the discharge flow channel 4. On the other hand, a WHRU side flow rate adjustment damper 45 that adjusts the flow rate of the exhaust gas flowing to the exhaust heat recovery channel 4b side is provided at a position downstream of the bypass channel side damper 43 of the exhaust heat recovery channel 4b.

Furthermore, a hot oil thermometer 461 which is a thermal fluid temperature measuring unit for measuring the temperature of the hot oil is provided in a flow path (thermal fluid flow path) through which the heated hot oil flowing out from the WHRU 46 flows. Further, the intake section 3 is provided with an intake thermometer 32 that is an intake temperature measuring section that measures the temperature of air taken from outside and cooled by the low-temperature heat exchange section 522.

In the present embodiment, the thermoacoustic engine side flow rate adjustment damper 44 and the WHRU side flow rate adjustment damper 45 are the hot oil temperature after heating measured by the hot oil thermometer 461, and after cooling measured by the intake air thermometer 32. The opening / closing operation (the flow rate adjusting operation of the exhaust gas flowing to the exhaust flow path 4 and the exhaust heat recovery flow path 4b) is executed based on a control signal from the control unit 6 that is output according to the air temperature (intake air temperature). .

Here, the hot oil heated by the WHRU 46 is used in various heating devices provided in the NG liquefaction facility, and is required to be stably heated to a predetermined temperature with little temperature fluctuation. Is done. Therefore, the control unit 6 opens and closes the thermoacoustic engine side flow rate adjustment damper 44 and the WHRU side flow rate adjustment damper 45 so that the hot oil temperature measured by the hot oil thermometer 461 approaches a preset target temperature. Execute.

Further, the temperature of the air taken into the intake section 3 and cooled by the low-temperature heat exchange section 522 only changes depending on the opening / closing operation of the thermoacoustic engine side flow rate adjustment damper 44 and the WHRU side flow rate adjustment damper 45. Not only will it change according to the outside air temperature. At this time, if the temperature of the air supplied to the air compressor 21 of the gas turbine 2 is excessively lowered, it may cause damage to the equipment. For example, from the viewpoint of preventing moisture freezing in an inlet guide vane (not shown) provided on the inlet side of the air compressor 21, the temperature of the air supplied to the inlet guide vane is, for example, 8 ° C. or higher. Is required.

From the viewpoint of device protection, the control unit 6 adds a predetermined margin to the preset lower limit temperature (for example, the temperature of the device constraint) as the temperature of the air after cooling measured by the intake thermometer 32. When the temperature falls below the temperature, the thermoacoustic engine side flow rate adjustment damper 44 and the WHRU side flow rate adjustment damper 45 are opened and closed so that the temperature of the cooled air becomes equal to or higher than the lower limit temperature.
Hereinafter, the operation of adjusting the flow rate of the exhaust gas to the exhaust passage 4 and the exhaust heat recovery passage 4b by the control unit 6 will be described with reference to FIG.

First, the gas turbine 2 is operated, the thermoacoustic engine side flow rate adjustment damper 44 and the WHRU side flow rate adjustment damper 45 are each adjusted to a predetermined opening degree, and the exhaust gas is discharged into the exhaust passage 4 and the exhaust heat recovery passage 4b. It is assumed that a predetermined flow rate is allocated (start).
The controller 6 determines whether or not the intake air temperature acquired from the intake thermometer 32 is equal to or higher than the lower limit temperature (step S101).

When the intake air temperature is equal to or higher than the lower limit temperature (step S101; YES), the hot oil temperature acquired from the hot oil thermometer 461 is within a preset target temperature range (temperature setting range). Is determined (step S102).
If the hot oil temperature is within the temperature setting range (step S102; YES), the intake air temperature confirmation (step S101) and the hot oil temperature confirmation (step S102) are repeated at predetermined time intervals.

When the temperature of the hot oil is out of the temperature setting range (step S102; NO), it is confirmed whether the temperature is equal to or higher than the upper limit value of the hot oil or lower than the lower limit value (step S103).

When the temperature of the hot oil is equal to or higher than the upper limit (step S103; YES), the WHRU side flow rate adjustment damper 45 is adjusted in a direction to close by a predetermined amount. Further, adjustment is performed to open the thermoacoustic engine side flow rate adjustment damper 44 by a predetermined amount so that the reduced amount of exhaust gas flows to the discharge flow path 4 side (step S105).

As a result, the flow rate of the exhaust gas passing through the WHRU 46 is reduced, and the temperature of the hot oil is lowered. On the other hand, the flow rate of the exhaust gas that passes through the high-temperature heat exchange unit 512 increases, and the intake air temperature decreases due to the action of the thermoacoustic engine 5.
After the appropriate adjustment is performed, the operations after step S101 are repeated.

On the other hand, when the temperature of the hot oil is equal to or lower than the lower limit value in step S103 (step S103; NO), the WHRU side flow rate adjustment damper 45 is adjusted to open by a predetermined amount. Further, adjustment is performed to close the thermoacoustic engine side flow rate adjustment damper 44 by a predetermined amount so that the increased amount of exhaust gas is transferred from the discharge flow path 4 side (step S104).

As a result, the flow rate of the exhaust gas that passes through the WHRU 46 increases and the temperature of the hot oil rises. On the other hand, the flow rate of the exhaust gas that passes through the high-temperature heat exchange unit 512 decreases, and the temperature of the air that is cooled via the thermoacoustic engine 5 (intake air temperature) increases.
After the appropriate adjustment is performed, the operations after step S101 are repeated.

If the intake air temperature acquired from the intake thermometer 32 is less than the lower limit temperature (step S101; NO), the thermoacoustic engine is used regardless of whether the temperature of the hot oil is within the temperature setting range. Adjustment for closing the side flow rate adjustment damper 44 by a predetermined amount is performed to reduce exhaust gas distributed to the discharge flow path 4 (step S104). As a result, the flow rate of the exhaust gas that passes through the high-temperature heat exchanging section 512 decreases, and the intake air temperature increases. Further, adjustment is performed to open the WHRU side flow rate adjustment damper 45 so that the exhaust gas flows to the exhaust heat recovery passage 4b side by the reduction amount of the exhaust passage 4 (step S104).

Thus, when the intake air temperature is lower than the lower limit temperature, the equipment can be protected by lowering the intake air temperature in preference to the exhaust gas flow rate adjustment for the purpose of temperature control on the hot oil side. it can. In this case, the flow rate of the exhaust gas passing through the WHRU 46 increases, the temperature of the hot oil rises, and the temperature upper limit value may be exceeded. Therefore, a trim cooler is provided on the downstream side of the flow path of hot oil flowing out from the WHRU 46. For hot oil that exceeds the upper temperature limit, the trim cooler is operated and cooled to the target temperature before being supplied to each device. Also good.

The embodiment described with reference to FIGS. 7 and 8 is a thermoacoustic that performs direct heating and cooling in which a high-temperature heat exchanging unit 512 and a low-temperature heat exchanging unit 522 are directly incorporated in the discharge flow path 4 and the intake portion 3, respectively. The application to the engine 5 is not limited. For example, the technique can also be applied to the thermoacoustic engine 5a that performs indirect heating and cooling shown in FIG.

Further, in the example described with reference to FIG. 8, in order to avoid frequent opening / closing operations of the thermoacoustic engine side flow rate adjustment damper 44 and the WHRU side flow rate adjustment damper 45, the target temperature range of the hot oil temperature is set. An example was given. However, the method for adjusting the temperature of the hot oil is not limited to this example. For example, PID control for opening and closing the WHRU side flow rate adjustment damper 45 may be performed so as to approach the target temperature value.
Furthermore, the thermal fluid generated by the WHRU 46 is not limited to hot oil but may be steam.

In addition, the configuration of the

thermoacoustic engines

5, 5a is not limited to the shape shown in FIGS. If generation of vibration in the first stack 51 and formation of a low temperature portion in the second stack 52 are possible, the first loop 51 is replaced with the first loop 51 instead of the heating loop loop 501 and the cooling loop 502. A stack 51 or a second stack 52 may be provided.

And the gas turbine 2 in which the intake air cooling is performed using the

thermoacoustic engines

5, 5a is not limited to the case where it is provided in the NG liquefaction facility. For example, with respect to the gas turbine 2 that drives the refrigerant compressor 10 that cools the refrigerant used in the natural gas processing facility that separates and recovers components such as condensate contained in NG, and the gas turbine 2 that drives the generator Thus, the above-described intake / exhaust device may be provided.

DESCRIPTION OF SYMBOLS 10 Refrigerant compressor 2 Gas turbine 21 Air compressor 22 Turbine 3 Intake part 4 Discharge flow path 501 Heating side loop pipe line 502 Cooling side loop pipe line 503 Connection pipe line 51 1st stack 511 Constant temperature heat exchange part 512 High temperature heat exchange Unit 52 second stack 521 constant temperature heat exchange unit 522 low temperature heat exchange unit 6 control unit

Claims

An intake exhaust system that cools air supplied to an air compressor provided in the gas turbine using exhaust gas exhausted from a gas turbine,
An intake section for taking in external air and supplying it to the air compressor;
An exhaust passage for exhausting exhaust gas exhausted from the gas turbine;
A stack that is an assembly of a plurality of flow paths that are narrower than the pipe line, and the other end side is heated to a higher temperature than the one end side in the pipe line in which the working gas is sealed. A first stack for generating a vibration in the gas, and provided on the downstream side in the propagation direction of the vibration generated in the first stack, along the propagation direction of the vibration. A thermoacoustic engine provided with a second stack for forming a low temperature part having a low temperature,
The other end side of the first stack is heated using the exhaust gas flowing through the discharge flow path, and the air taken into the intake portion uses the low temperature part on the other end side of the second stack. Intake and exhaust system, which is cooled by cooling.
The other end side of the first stack is provided with a high-temperature heat exchanging section for exchanging heat between the exhaust gas flowing through the discharge passage and the working gas in the pipe. The intake / exhaust device according to claim 1.
The low-temperature heat exchange part for performing heat exchange between the air taken into the intake part and the low-temperature part is provided on the other end side of the second stack. Intake and exhaust system as described in 1.
The exhaust passage is provided with a heating medium heating unit for heating the heating medium by heat exchange with the exhaust gas, and the other end side of the first stack is heated by the heating medium heating unit. The intake / exhaust device according to claim 1, further comprising a high-temperature heat exchanging section for exchanging heat between the heat medium and the working gas in the pipe.
The other end of the second stack is provided with a low temperature heat exchange part for cooling the refrigerant by heat exchange with the low temperature part, and the intake part is cooled by the low temperature heat exchange part. The intake / exhaust device according to claim 1, further comprising an air cooling unit that cools the air taken into the intake unit by heat exchange with the refrigerant.
A first discharge flow path that is the discharge flow path related to the heating of the other end side of the first stack using the exhaust gas;
A second discharge flow path for discharging the exhaust gas without heating the other end of the first stack;
A switching mechanism for switching a destination of exhaust gas exhausted from the gas turbine between the first discharge channel and the second discharge channel,
When the output of the gas turbine is greater than or equal to a preset intake air cooling output, the switching mechanism uses the exhaust gas exhaust destination as a first exhaust passage, and the output of the gas turbine is greater than the intake air cooling output. 2. The intake / exhaust device according to claim 1, wherein the exhaust flow path is switched so that the exhaust gas is discharged to the second discharge flow path when the exhaust gas is discharged.
The intake / exhaust device according to claim 6, wherein the intake cooling output is set to a value within a range of 50% or more and less than 100% of a rated output of the gas turbine.
A first discharge flow path that is the discharge flow path related to the heating of the other end side of the first stack using the exhaust gas;
An exhaust heat recovery unit for branching from the first exhaust flow path upstream from a position for heating the other end side of the first stack and heating the thermal fluid by the exhaust gas is provided. A second discharge channel;
The flow rate adjustment mechanism which performs flow rate adjustment which distributes the exhaust gas exhausted from the gas turbine to the 1st discharge channel and the 2nd discharge channel, The above-mentioned is provided. Intake and exhaust system.
A thermal fluid passage through which the heated thermal fluid flowing out of the exhaust heat recovery section flows,
A thermal fluid temperature measurement unit that measures the temperature of the thermal fluid flowing through the thermal fluid flow path,
The flow rate adjusting mechanism is configured to discharge a part of the exhaust gas exhausted from the gas turbine so that the temperature of the thermal fluid measured by the thermal fluid temperature measurement unit approaches a predetermined target temperature. The intake / exhaust device according to claim 8, wherein the flow rate of the exhaust gas flowing through the flow path is adjusted, and the remaining exhaust gas is distributed to the first discharge flow path.
An intake air temperature measurement unit that measures the temperature of the air taken into the intake unit and cooled by using the low temperature part;
When the temperature of the cooled air measured by the intake air temperature measurement unit is lower than a preset lower limit temperature, the air flow adjusting mechanism has a temperature of the cooled air that is equal to or higher than the lower limit temperature. The exhaust gas distributed to the first discharge flow path is reduced so that the flow rate of the exhaust gas flowing through the exhaust gas to the second discharge flow path side is increased by the decrease of the first discharge flow path. The intake / exhaust device according to claim 8.
The gas turbine is provided in a natural gas processing facility for liquefying natural gas or separating / recovering components in natural gas, and drives a refrigerant compressor that compresses a natural gas processing refrigerant for cooling the natural gas. The intake / exhaust device according to claim 1, wherein
In natural gas processing facilities that liquefy natural gas or separate and recover components in natural gas,
A refrigerant compressor for compressing a natural gas processing refrigerant for cooling the natural gas;
A gas turbine for driving the refrigerant compressor;
A natural gas processing facility comprising the intake / exhaust device according to any one of claims 1 to 11.