WO2016009658A1

WO2016009658A1 - Compressor system, subsea production system provided therewith, and compressor cleaning method

Info

Publication number: WO2016009658A1
Application number: PCT/JP2015/051529
Authority: WO
Inventors: 勇哉紺野; 伊藤　栄基
Original assignee: 三菱重工業株式会社
Priority date: 2014-07-18
Filing date: 2015-01-21
Publication date: 2016-01-21
Also published as: US20170198724A1; JP2016023578A; CN106489029A; EP3156665A4; EP3156665A1

Abstract

This compressor system is provided with a compressor (50) that comprises a casing, a rotation shaft supported inside the casing, and an impeller which compresses air by rotating together with the rotation shaft. The compressor system is provided with a compressed air circulation unit (52) which circulates air compressed by the compressor (50), a hydrate freezing prevention agent supply unit (53) which supplies to the compressed air circulation unit (52) a hydrate freezing prevention agent that prevents the aforementioned gas from forming hydrates, and an inner hydrate freezing prevention agent supply unit (54) which supplies to an inner flow path of the compressor (50) a portion of the aforementioned hydrate freezing prevention agent.

Description

Compressor system, undersea production system equipped with the same, and compressor cleaning method

The present invention relates to a compressor system, an undersea production system including the compressor system, and a compressor cleaning method.

In the underwater production system that mines seabed resources, production fluid mixed with crude oil, natural gas, etc. is pumped from a production well drilled to a depth of several thousand meters from the seabed. In the undersea production system, the pumped production fluid is separated into a gas such as natural gas and a liquid such as crude oil by a separator such as a scrubber, and then sent to a ship on the sea via a flow line extending in the sea. At this time, in order to send a gas such as natural gas to a ship on the sea, a compressor installed on the seabed is used.

In such a compressor installed on the seabed, deposits accumulate in the internal flow path through which natural gas circulates due to continuous operation. As a result, the flow rate of natural gas that can be circulated through the internal flow path is lowered, and the efficiency as a compressor is lowered.

For such a compressor, for example, Patent Document 1 discloses a cleaning method in which a part of condensate, which is a hydrocarbon contained in a liquid separated by a separator, is supplied to the compressor for cleaning. In this compressor cleaning method, condensate decomposes and removes deposits to clean the internal flow path of the compressor.

International Publication No. 2013/185801

However, the above-described cleaning method uses condensate collected from the production well. Therefore, with this cleaning method, there is a possibility that a necessary amount of condensate cannot be collected stably from the production well. As a result, it is difficult to stably clean the compressor.

The present invention provides a compressor system capable of stably cleaning a compressor, an undersea production system including the compressor system, and a compressor cleaning method.

In order to solve the above problems, the present invention proposes the following means.
A compressor system according to a first aspect of the present invention includes a compressor having a casing, a rotating shaft supported in the casing, and an impeller that rotates together with the rotating shaft to compress gas. A compressed gas flow part through which the gas compressed in the flow passes, a hydrate antifreeze supply part that supplies the compressed gas flow part with a hydrate antifreeze agent that suppresses hydration of the gas, and the hydrate freeze prevention An internal hydrate antifreeze supplying part for supplying a part of the hydrate antifreeze supplied by the agent supplying part to an internal flow path formed by the impeller and the casing.

According to such a configuration, in order to suppress the hydrate formation of the gas compressed by the compressor, a part of the hydrate antifreeze agent supplied from the hydrate antifreeze agent supply unit to the compressed gas circulation unit is an internal flow path. To be supplied. Therefore, the hydrate antifreeze flows along with the gas in the internal flow path, and the deposits accumulated in the internal flow path can be removed. By supplying the hydrate antifreeze directly to the internal flow path, it is possible to prevent the hydrate antifreeze from being diluted by gas before reaching the internal flow path, and effectively use the hydrate antifreeze. It is possible to clean the inside of the compressor. By using a part of the hydrate antifreeze supplied from the hydrate antifreeze supply part to the compressed gas circulation part, the required amount of hydrate antifreeze can be stably supplied to the internal flow path. Can do.

In the compressor system, when a predetermined condition is satisfied, supply control is performed so that the internal hydrate antifreeze supplying unit starts supplying the hydrate antifreeze to the internal flow path. You may provide the control part.

According to such a configuration, by controlling the supply of the hydrate antifreeze by the control unit, the hydrate antifreeze can be supplied in a limited manner to a compressor that requires cleaning. . Therefore, the hydrate antifreeze supplied from the internal hydrate antifreeze supplier can be efficiently used for cleaning the compressor, and the supply amount of the hydrate antifreeze can be suppressed.

In the compressor system, the control unit determines whether or not a difference between the characteristic values of the gas between the inlet side of the compressor and the outlet side of the compressor satisfies a predetermined first criterion. And when the first reference determination unit determines that the first reference is satisfied, the hydrate to the internal flow path with respect to the internal hydrate antifreeze supply unit is determined. A supply start instructing unit that sends an instruction to start the supply of the rate freeze inhibitor.

According to such a configuration, by calculating the difference from the characteristic value of the gas on the inlet side and the outlet side of the compressor, and determining by comparing with the first reference predetermined by the first reference determination unit, It can be easily estimated whether or not the internal flow path is in a state that requires cleaning. The supply start instructing unit starts supplying the hydrate antifreeze to the internal flow path based on the determination result, whereby the internal flow path can be cleaned. Therefore, it can be determined with high accuracy whether or not the compressor is in a state requiring cleaning, and the hydrate antifreeze can be supplied more limitedly. As a result, the hydrate antifreeze supplied from the internal hydrate antifreeze supply unit can be used more efficiently for cleaning the compressor with respect to the internal flow path that requires cleaning. The supply amount of the antifreezing agent can be further suppressed.

The compressor system includes a heating unit that heats the hydrate antifreeze agent, and the internal hydrate antifreeze supply unit supplies the hydrate antifreeze agent heated by the heating unit to the internal flow path. You may supply.

According to such a configuration, the high temperature hydrate antifreezing agent can be supplied to the internal flow path by providing the heating unit. By being heated to a high temperature, the solubility of the hydrate antifreeze in the deposit can be improved. Therefore, the dissolution rate of the deposit accumulated in the internal channel can be improved, and the internal channel can be effectively cleaned.

The compressor system includes a heating unit that heats the hydrate antifreeze agent, and the control unit opens the inlet of the compressor after opening the supply of the hydrate antifreeze agent to the internal flow path. A second reference determination unit that determines whether or not a difference between the characteristic value of the gas on the outlet side and the outlet side of the compressor satisfies a predetermined second reference, and the second reference determination unit When it is determined that the second standard is satisfied, the internal hydrate antifreeze supply unit is instructed to supply the internal flow path with the hydrate antifreeze heated by the heating unit. You may have the heating supply instruction | indication part to send.

According to such a configuration, a difference is calculated from the characteristic values of the gas on the inlet side and the outlet side of the compressor, and the internal flow is again determined by comparing the second reference determination unit with the second reference. It can be easily estimated whether or not the road is in a state requiring cleaning. Therefore, for example, it is possible to easily estimate the state of the internal flow path that is different from the case of determination using the first reference. Based on the determination result, the heating supply instruction unit sends an instruction to supply the hydrate antifreezing agent heated by the heating unit to the internal flow path, so that the hydrate antifreezing agent heated to a high temperature is The flow path can be more effectively cleaned. Therefore, powerful cleaning can be performed on the compressor as needed. As a result, when the internal flow path is in a state that requires strong cleaning, the heated hydrate antifreeze can be efficiently supplied and the compressor can be cleaned more efficiently.

The subsea production system according to the second aspect of the present invention includes the compressor system and a separator that separates the production fluid pumped from the production well into the gas and the liquid and supplies the gas and liquid to the compressor.

According to such a configuration, even a compressor installed at a position where maintenance is difficult, such as the seabed, can be stably and efficiently washed. Therefore, clogging due to the deposit can be suppressed, and the gas can be stably sent to the gas by the compressor.

A compressor cleaning method according to a third aspect of the present invention cleans a compressor having a casing, a rotating shaft supported in the casing, and an impeller that rotates together with the rotating shaft to compress gas. In the compressor cleaning method, a first determination is made as to whether or not a difference in the characteristic value of the gas between the inlet side of the compressor and the outlet side of the compressor satisfies a predetermined first criterion. When it is determined that the first reference is satisfied in the reference determination step and the first reference determination step, the internal flow path formed by the impeller and the casing is compressed by the compressor. A supply start step of starting supply of a hydrate antifreeze agent that suppresses hydration of the gas supplied to the gas.

According to such a configuration, a difference is calculated from the gas characteristic values on the inlet side and the outlet side of the compressor, and the internal flow path is determined by comparing with the first reference in the first reference determining step. It can be easily estimated whether or not is in a state that requires cleaning. The internal flow path can be cleaned by starting the supply of the hydrate antifreeze to the internal flow path in the supply start step based on the determination result. Therefore, it can be determined with high accuracy whether or not the compressor is in a state requiring cleaning, and the hydrate antifreeze can be supplied more limitedly. As a result, the hydrate antifreeze supplied from the internal hydrate antifreeze supply unit can be used more efficiently for cleaning the compressor with respect to the internal flow path that requires cleaning. The supply amount of the antifreezing agent can be further suppressed.

In the compressor cleaning method, after releasing the supply of the hydrate antifreeze to the internal flow path, the gas characteristic values of the inlet side of the compressor and the outlet side of the compressor are The second reference determination step for determining whether or not the difference satisfies a predetermined second criterion, and when it is determined that the second criterion is satisfied in the second reference determination step, the heated A heating and supplying step of supplying a hydrate antifreeze to the internal flow path.

According to such a configuration, a difference is calculated from the gas characteristic values on the inlet side and the outlet side of the compressor, and the internal flow is again determined by comparing with the second reference in the second reference determining step. It can be easily estimated whether or not the road is in a state requiring cleaning. For example, it is possible to easily estimate whether the state of the internal flow path is different from that determined using the first reference (for example, whether the internal flow path needs stronger cleaning). it can. Based on the determination result, the hydrate antifreeze that has been heated to a high temperature is supplied from the hydrate antifreeze injection part to the internal flow path in the heating supply process, thereby cleaning the internal flow path more effectively. Can be implemented. Therefore, powerful cleaning can be performed on the compressor as needed. As a result, when the internal flow path is in a state that requires strong cleaning, the heated hydrate antifreeze can be efficiently supplied and the compressor can be cleaned more efficiently.

According to the present invention, the compressor can be efficiently cleaned by supplying the hydrate antifreeze to the internal flow path.

It is a mimetic diagram explaining an undersea production system in an embodiment of the present invention. It is a distribution diagram explaining a subsea module in an embodiment of the present invention. It is principal part sectional drawing explaining the internal flow path of the compressor in embodiment of this invention. It is process drawing explaining the washing | cleaning method of the compressor in embodiment of this invention.

Hereinafter, embodiments according to the present invention will be described with reference to FIGS. 1 to 4.
The undersea production system 1 according to the embodiment of the present invention is a Subsea Production System that is one of the offshore oil and gas field development methods. As shown in FIG. 1, the undersea production system 1 is a production well W that collects a production fluid PF that mixes crude oil O, natural gas G, and the like mined from an oil and gas field F existing at several hundred to several thousand meters in the seabed. A manifold M that collects and branches the production fluid PF collected at the production well W, a flow line FL that is a pipe that conveys the production fluid PF branched by the manifold M, and a production fluid PF that is conveyed by the flow line FL. A subsea module SM that separates liquid and gas and sends them to the sea is provided. The undersea production system 1 is moored at sea, a riser R that is a pipe that carries crude oil O and natural gas G from the subsea module SM to the sea, an umbilical line AL that is a cable that supplies power to the subsea module SM, etc. A riser R and an umbilical line AL are connected to each other, and a ship S for storing crude oil O and natural gas G is provided.

Manifold M is installed in the vicinity of production well W of submarine oil and gas field F. The manifold M is a device that transports the mined production fluid PF to a plurality of flow lines FL by collecting and branching.

The flow line FL is a pipeline that pumps the production fluid PF from the manifold M to the subsea module SM by the pressure energy of the oil and gas field F.

The riser R extends from the subsea module SM on the sea floor to the ship S on the sea. The riser R of the present embodiment includes an oil pipeline OR that conveys crude oil O sent from the subsea module SM to a storage tank (not shown) disposed on the marine vessel S, and a natural gas G sent from the subsea module SM. Is separately provided with a gas pipeline GR for conveying the gas to the storage tank. The riser R also has a pipeline AR for hydrate antifreeze that supplies hydrate antifreeze from the ship S to the gas pipeline GR that supplies natural gas G so that the natural gas G does not freeze due to hydrate formation on the sea floor. Is provided.

The umbilical line AL is a composite cable having a power cable, a hydraulic cable, and a signal cable for controlling the subsea module SM. The umbilical line AL sends power and signals from a generator (not shown) on the ship S to the subsea module SM and the manifold M.

The subsea module SM separates the production fluid PF supplied via the flow line FL into a gas and a liquid, and pumps the gas and the liquid to the sea respectively. As shown in FIG. 2, the subsea module SM of the present embodiment gasses the main heat exchanger 2 that cools the production fluid PF pumped up from the production well W and the production fluid PF that is cooled by the main heat exchanger 2. And a separator 3 for separating the liquid into the liquid, a pump system 4 for sending the liquid separated by the separator 3 to the riser R, and a compressor system 5 for sending the gas separated by the separator 3 to the riser R.

The main heat exchanger 2 cools the high-temperature production fluid PF pumped from the production well W and sent through the flow line FL to a temperature that can be used by the separator 3. The main heat exchanger 2 of the present embodiment cools the production fluid PF by exchanging heat with low-temperature seawater on the seabed.

The separator 3 separates the production fluid PF into natural gas G that is a gas and crude oil O that is a liquid. The separator 3 of this embodiment is a scrubber. The separator 3 separates the natural gas G and the crude oil O containing condensate from the production fluid PF. The separator 3 sends the separated crude oil O to the pump system 4. The separator 3 sends the separated natural gas G to the compressor system 5.

The pump system 4 compresses the crude oil O sent from the separator 3 and sends it to the oil pipeline OR. As shown in FIG. 2, the pump system 4 includes a pump 41 that compresses crude oil O, a liquid circulation part 42 that sends the crude oil O from the separator 3 to the pump 41, and a compressed liquid in which crude oil O compressed by the pump 41 circulates. A distribution unit 43.

The pump 41 compresses the sent crude oil O and sends it out.
The liquid circulation unit 42 supplies the crude oil O from the separator 3 to the pump 41. Specifically, the liquid circulation part 42 of the present embodiment is a pipe connected from the separator 3 to the pump 41. In the liquid circulation part 42, crude oil O circulates inside.
The compressed liquid circulation unit 43 sends the crude oil O compressed by the pump 41 to the oil pipeline OR. Specifically, the compressed liquid circulation part 43 of this embodiment is a pipe connected from the pump 41 to the oil pipeline OR. The compressed liquid circulation part 43 circulates the crude oil O compressed inside.

Compressor system 5 compresses natural gas G sent from separator 3 and sends it to gas pipeline GR. As shown in FIG. 2, the compressor system 5 includes a compressor 50 that compresses the natural gas G, a gas flow part 51 that sends the natural gas G from the separator 3 to the compressor 50, and the natural gas compressed by the compressor 50. Compressed gas circulation section 52 through which gas G circulates, hydrate antifreeze supply section 53 that supplies hydrate antifreeze agent that suppresses hydration of natural gas G to compressed gas circulation section 52, and hydrate antifreeze agent An internal hydrate antifreeze supply unit 54 that supplies a part of the hydrate antifreeze supplied by the supply unit 53 to the compressor 50, a heating unit 55 that heats the hydrate antifreeze, and an internal hydrate antifreeze And a control unit 60 that performs supply control for starting supply of the hydrate antifreeze agent to the agent supply unit 54.

The compressor 50 is a multistage centrifugal compressor including a plurality of impellers 503. As shown in FIG. 3, the compressor 50 of the present embodiment includes a casing 501 in which an internal flow path FC for flowing gas from the upstream side to the downstream side is formed, and is supported around the casing 501 and rotates about the axis SL. A rotating shaft 502 to be rotated, and an impeller 503 that rotates together with the rotating shaft 502 to compress gas.

The casing 501 is a stationary body and has a cylindrical shape. The casing 501 has a rotation shaft 502 disposed so as to penetrate the center. The casing 501 is provided with a bearing device (not shown). The bearing device supports the rotating shaft 502 to be rotatable.

The rotating shaft 502 is a rotating body, has a columnar shape, and extends in the axis SL direction in which the axis SL extends.
The impeller 503 is a rotating body, and a plurality of impellers 503 are provided at intervals in the direction of the axis SL of the rotating shaft 502. Each impeller 503 compresses the natural gas G (gas) using centrifugal force due to rotation. The impeller 503 includes a disk 503a, a blade 503b, and a cover 503c. The impeller 503 is a so-called closed impeller 503.

The disks 503a are each formed in a disk shape that gradually increases in diameter radially outward of the rotating shaft 502 toward the downstream side that is one side of the rotating shaft 502 in the axis SL direction.
The blade 503b is formed so as to protrude from the disk 503a to the upstream side in the axis SL direction, which is the opposite side to the downstream side in the axis SL direction. A plurality of blades 503b are formed on the disk 503a at predetermined intervals in the circumferential direction of the axis SL.
The cover 503c covers the plurality of blades 503b from the upstream side in the axis SL direction.
The cover 503c is formed in a disk shape facing the disk 503a.

The internal flow path FC is formed by the impeller 503 and the casing 501 so as to connect the impellers 503 so that the natural gas G is compressed stepwise. The internal flow path FC includes a compression flow path FC1 defined by the impeller 503, and a casing flow path FC2 that is formed in the casing 501 and adjusts the flow of the natural gas G.

The compression flow path FC1 is defined by a surface facing the upstream side in the axis SL direction of the disk 503a, a surface facing the downstream side in the axis SL direction of the cover 503c, and a surface facing the circumferential direction of the blade 503b. .
The casing flow path FC2 adjusts the flow of the natural gas G in order to flow the natural gas G to the compression flow path FC1 defined by the impeller 503.

The gas circulation part 51 supplies the natural gas G from the separator 3 to the compressor 50. Specifically, the gas circulation part 51 of this embodiment is piping connected from the separator 3 to the compressor 50 as shown in FIG. In the gas circulation part 51, the natural gas G circulates inside. The gas flow unit 51 of the present embodiment has an inlet side characteristic value measuring unit 511 that measures the characteristic value of the natural gas G on the inlet side of the compressor 50.

The inlet side characteristic value measuring unit 511 measures the characteristic value of the natural gas G flowing into the compressor 50. The inlet side characteristic value measuring unit 511 is provided in the vicinity of the inlet of the compressor 50 of the gas circulation unit 51. The inlet side characteristic value measuring unit 511 of the present embodiment is a pressure sensor that measures a pressure value as a characteristic value. The inlet side characteristic value measuring unit 511 transmits the measured pressure value of the natural gas G to the control unit 60.

The compressed gas circulation part 52 sends the natural gas G compressed by the compressor 50 to the riser R. Specifically, the compressed gas circulation part 52 of this embodiment is piping connected from the compressor 50 to the gas pipeline GR. The compressed gas circulation part 52 circulates the natural gas G compressed inside. The compressed gas circulation unit 52 of the present embodiment has an outlet side characteristic value measuring unit 521 that measures a characteristic value of the natural gas G that is a gas on the outlet side of the compressor 50.

The outlet side characteristic value measuring unit 521 measures the characteristic value of the natural gas G flowing out from the compressor 50. The outlet side characteristic value measuring unit 521 is provided in the vicinity of the outlet of the compressor 50 of the compressed gas circulation unit 52. The outlet side characteristic value measuring unit 521 of the present embodiment is a pressure sensor that measures a pressure value as a characteristic value, like the inlet side characteristic value measuring unit 511. The outlet side characteristic value measuring unit 521 transmits the measured pressure value of the natural gas G to the control unit 60.

The hydrate antifreeze supply unit 53 distributes the hydrate antifreeze supplied from the marine vessel S through the hydrate antifreeze pipeline AR to the compressed gas circulation unit 52. The hydrate antifreeze supply unit 53 of this embodiment is a pipe connected to the compressed gas circulation unit 52 from the hydrate antifreeze pipeline AR. In the hydrate antifreeze supply unit 53, the hydrate antifreeze flows through the inside. The hydrate antifreeze supply unit 53 is connected to the downstream side of the position where the outlet side characteristic value measurement unit 521 of the compressed gas circulation unit 52 is provided.
In addition, as the hydrate antifreeze of this embodiment, it is preferable to use a fluid having lipophilicity or hydrophilicity. As the hydrate antifreeze, for example, it is particularly preferable to use monoethylene glycol which is used for preventing the hydrate formation of the natural gas G and suppressing the hydrate formation.

The internal hydrate antifreeze supplying unit 54 supplies a part of the hydrate antifreeze flowing through the hydrate antifreeze supplying unit 53 to the internal flow path FC of the compressor 50. Specifically, the internal hydrate antifreeze supply unit 54 of the present embodiment includes a first supply pipe 541 and a first supply valve 542 that adjusts the flow of the hydrate antifreeze flowing through the first supply pipe 541. The second supply pipe 543 branched from the first supply pipe 541 and the second supply valve 544 for adjusting the flow of the hydrate antifreeze flowing through the second supply pipe 543 are provided.

The first supply pipe 541 branches from the hydrate antifreeze supply unit 53 and is connected to the casing 501 of the compressor 50. Specifically, the first supply pipe 541 of the present embodiment is connected so as to pass through the casing 501 of the compressor 50. The first supply pipe 541 is branched in the casing 501. The first supply pipe 541 is provided with a hydrate antifreeze injection portion 541a for injecting a hydrate antifreeze toward the casing flow path FC2 at the tip portion.

The first supply valve 542 adjusts the supply of the hydrate antifreeze to the inside of the first supply pipe 541. Specifically, the first supply valve 542 of the present embodiment is closed to stop the supply of the hydrate antifreeze into the first supply pipe 541 and is opened to open the first supply pipe 541. The supply of hydrate antifreeze to the inside is started. The first supply valve 542 is an electromagnetic valve whose opening and closing operations are controlled by the control unit 60.

The second supply pipe 543 branches from the first supply pipe 541 and supplies a hydrate antifreeze to the compressor 50. The second supply pipe 543 of this embodiment branches from the first supply pipe 541 on the upstream side of the position where the first supply valve 542 is provided, and is downstream of the position where the first supply valve 542 is provided. It is again connected to the first supply pipe 541 on the side.

The second supply valve 544 adjusts the supply of the hydrate antifreeze to the inside of the second supply pipe 543. Specifically, the second supply valve 544 of the present embodiment is closed to stop the supply of the hydrate antifreeze into the second supply pipe 543, and is opened to release the second supply pipe 543. The supply of hydrate antifreeze to the inside is started. The second supply valve 544 is an electromagnetic valve whose opening and closing operations are controlled by the control unit 60.

The heating unit 55 is provided in the internal hydrate antifreeze supplying unit 54 and heats the hydrate antifreeze. The heating part 55 of the present embodiment is provided at a position where the second supply pipe 543 and the liquid circulation part 42 intersect on the downstream side of the second supply valve 544 of the second supply pipe 543. The heating unit 55 uses the heat of the crude oil O flowing through the pump system 4 to heat the hydrate antifreeze. Specifically, the heating unit 55 has a high temperature of 110 ° C. or higher, for example, monoethylene glycol, which is a hydrate antifreeze flowing in the second supply pipe 543 at an ambient temperature of about 20 ° C. to 50 ° C. Until heated.

The control unit 60 causes the internal hydrate antifreeze supply unit 54 to start supplying the hydrate antifreeze to the internal flow path FC of the compressor 50 when a predetermined condition is satisfied. I do. The control unit 60 of the present embodiment controls the opening and closing operations of the first supply valve 542 and the second supply valve 544 when a predetermined condition is satisfied, so that the hydrate to the internal flow path FC is controlled. The supply of antifreeze is controlled.

Specifically, the control unit 60 of the present embodiment has a first input unit 61 to which a characteristic value measured by the inlet side characteristic value measuring unit 511 is input, and a characteristic value measured by the outlet side characteristic value measuring unit 521. A second input unit 62 that is input; and a difference calculation unit 63 that calculates a difference between the characteristic value input to the first input unit 61 and the characteristic value input to the second input unit 62. . The control unit 60 of the present embodiment includes a first reference determination unit 64 that determines whether or not the difference calculated by the difference calculation unit 63 satisfies a predetermined first reference, and a determination by the first reference determination unit 64. And a supply start instructing unit 65 for sending an instruction to start the supply of the hydrate antifreeze to the internal flow path FC based on the result. The control unit 60 of the present embodiment includes a second reference determination unit 66 that determines whether or not the difference calculated by the difference calculation unit 63 satisfies a predetermined second reference, and a determination by the second reference determination unit 66. Based on the determination result of the second reference determination unit 66 and the heating supply instruction unit 67 that sends an instruction to supply the hydrate antifreeze agent heated by the heating unit 55 to the internal flow path FC based on the result. And a cleaning end instruction unit 70 for sending an instruction to end the supply of the hydrate antifreeze to the flow path FC. The controller 60 of the present embodiment opens or closes the first supply valve 542 based on the input signal, and opens or closes the second supply valve 544 based on the input signal. And a second supply valve instruction unit 69 to be closed.

The first input unit 61 receives the pressure value of the natural gas G measured by the inlet side characteristic value measuring unit 511. The first input unit 61 outputs information on the input pressure value to the difference calculation unit 63.
The pressure value of the natural gas G measured by the outlet side characteristic value measuring unit 521 is input to the second input unit 62. The second input unit 62 outputs the input pressure value information to the difference calculation unit 63.

The difference calculation unit 63 calculates a difference obtained by subtracting the pressure value on the inlet side of the compressor input by the first input unit 61 from the pressure value on the outlet side of the compressor input by the second input unit 62. The difference calculation unit 63 outputs the calculated difference to the first reference determination unit 64. The difference calculation unit 63 outputs the calculated difference to the second reference determination unit 66 when information is input again from the first input unit 61 and the second input unit 62 after being output to the first reference determination unit 64. Output.

The first reference determination unit 64 compares the difference information input from the difference calculation unit 63 with the first reference. Here, the first standard is a value indicating that deposits are deposited and the internal flow path FC of the compressor 50 is narrow, and cleaning is necessary. The first reference of the present embodiment is set to a value smaller than the increase value of the pressure of the natural gas G that is compressed by flowing through the compression channel FC1 in the normal state when cleaning is not necessary. That is, the first reference of the present embodiment is that the difference in pressure between the inlet side and the outlet side of the compressor 50 in a state where the internal channel FC is narrowed by the deposit and the natural gas G is hardly compressed. Value.

The first reference determination unit 64 of this embodiment determines whether or not the input difference value is below the first reference. The first reference determination unit 64 sends a signal to the supply start instruction unit 65 when it is determined that the calculated difference is less than the first reference and satisfies the first reference.

When the supply start instruction unit 65 determines that the first reference is satisfied by the first reference determination unit 64, the supply start instruction unit 65 prevents the hydrate freeze prevention to the internal flow path FC with respect to the internal hydrate antifreeze supply unit 54. Send instructions to start the agent supply. The supply start instruction unit 65 according to the present embodiment sends a signal to the first supply valve instruction unit 68 and sends an instruction to the first supply valve 542 when a signal is input from the first reference determination unit 64.

The second reference determination unit 66 compares the difference information input from the difference calculation unit 63 with the second reference. Here, the second standard is a value indicating that the deposits in the internal flow path FC of the compressor 50 are not sufficiently removed and a stronger cleaning is necessary. The second reference of the present embodiment is set to a value that is smaller than the increase value of the pressure of the natural gas G compressed by flowing through the compression passage FC1 in the normal state and larger than the first reference. That is, the second standard of the present embodiment is a state in which deposits remain in the internal flow path FC and the natural gas G is not sufficiently compressed as a result of being washed once but not so much as to satisfy the first standard. This is the value of the difference in pressure between the inlet side and the outlet side of the compressor 50.

The second reference determination unit 66 of the present embodiment determines whether or not the input difference value is below the second reference. The second reference determination unit 66 sends a signal to the heating supply instruction unit 67 when it is determined that the calculated difference is less than the second reference and satisfies the second reference. The second reference determination unit 66 sends a signal to the cleaning end instruction unit 70 when it is determined that the calculated difference exceeds the second reference and does not satisfy the second reference.

When the heat supply instructing unit 67 determines that the second reference is satisfied by the second reference determining unit 66, the hydrate freezing heated by the heating unit 55 with respect to the internal hydrate antifreeze supply unit 54 is performed. An instruction is sent to supply the inhibitor to the internal flow path FC. The heating supply instruction unit 67 of this embodiment receives a signal from the second reference determination unit 66. As a result, the heating supply instruction unit 67 sends a signal to the first supply valve instruction unit 68 and the second supply valve instruction unit 69 after the signal is sent from the supply start instruction unit 65, and the first supply valve 542 and the second supply valve instruction unit 69. An instruction is sent to each of the two supply valves 544.

When the second reference determination unit 66 determines that the second reference is not satisfied, the cleaning end instruction unit 70 prevents the internal hydrate antifreeze supply unit 54 from hydrate freezing into the internal flow path FC. Send instructions to end the supply of agent. The cleaning end instruction unit 70 of this embodiment receives a signal from the second reference determination unit 66. As a result, the cleaning end instruction unit 70 sends a signal to the first supply valve instruction unit 68 and the second supply valve instruction unit 69, and sends instructions to the first supply valve 542 and the second supply valve 544, respectively.

The first supply valve instruction unit 68 sends an instruction to open the first supply valve 542 when a signal is input from the supply start instruction unit 65. The first supply valve instruction unit 68 sends an instruction to close the first supply valve 542 when a signal is input from the heating supply instruction unit 67. The first supply valve instruction unit 68 sends an instruction to close the first supply valve 542 when a signal is input from the cleaning end instruction unit 70.

The second supply valve instruction unit 69 sends an instruction to open the second supply valve 544 when a signal is input from the heating supply instruction unit 67. The second supply valve instruction unit 69 sends an instruction to close the second supply valve 544 when a signal is input from the cleaning end instruction unit 70.

Next, the operation of the undersea production system 1 of the above embodiment will be described.
The undersea production system 1 of the present embodiment collects the production fluid PF collected from the oil and gas field F through the production well W in the manifold M, and uses the pressure energy when mined from the oil and gas field F in the flow line FL. Is supplied to the subsea module SM.

In the subsea module SM, power is supplied to each device by a umbilical line AL from a generator (not shown) on the ship S. The production fluid PF supplied to the subsea module SM is cooled by the main heat exchanger 2 and flows into the separator 3. The production fluid PF that has flowed into the separator 3 is separated into crude oil O that is liquid and natural gas G that is gas.
The crude oil O separated by the separator 3 includes condensate and the like.

Crude oil O separated by the separator 3 circulates in the liquid circulation part 42 and is sent to the pump 41. The pump 41 compresses the crude oil O, sends it to the oil pipeline OR through the compressed liquid circulation section 43, and supplies it to a storage tank for crude oil O (not shown) on the ship S.

The natural gas G separated by the separator 3 circulates in the liquid circulation part 42 and is sent to the compressor 50. In the compressor 50, when the natural gas G flows through the internal flow path FC, the impeller 503 rotates together with the rotating shaft 502, whereby the natural gas G is compressed in the compression flow path FC1 and sent to the compressed gas flow section 52. It is done. A hydrate antifreeze is supplied from the hydrate antifreeze supply unit 53 to the compressed gas circulation unit 52. A hydrate antifreeze agent is fed into the gas pipeline GR together with the compressed natural gas G. In the compressed gas circulation part 52, the natural gas G is supplied to a storage tank (not shown) for the natural gas G on the ship S while being prevented from being hydrated by the supplied hydrate antifreeze.

Next, a method for cleaning the compressor 50 according to the above embodiment will be described.
As described above, in the compressor 50 that compresses the natural gas G and supplies the compressed gas to the ship S, the deposit is deposited and accumulated in the internal flow path FC through which the natural gas G flows. In the cleaning method of the compressor 50, the compressor 50 in which the deposits are accumulated is cleaned. A method for cleaning the compressor 50 according to the present embodiment will be described with reference to FIGS.

In the cleaning method for the compressor 50 of the present embodiment, as shown in FIG. 4, the pressure value is measured as a characteristic value of the natural gas G that is a gas separated by the separator 3 on the inlet side and the outlet side of the compressor 50. And the state of the compressor 50 is measured (characteristic value acquisition step S100). Specifically, in the characteristic value acquisition step S100, the pressure value of the natural gas G flowing through the gas flow unit 51 is measured by the inlet-side characteristic value measurement unit 511, and the pressure value of the natural gas G on the inlet side of the compressor 50 is measured. To get. The pressure value of the natural gas G flowing through the compressed gas flow unit 52 is measured by the outlet side characteristic value measuring unit 521, and the pressure value of the natural gas G on the outlet side of the compressor 50 is acquired.

Next, in the cleaning method for the compressor 50 of the present embodiment, the difference between the acquired pressure value on the inlet side and the pressure value on the outlet side of the compressor 50 is calculated (difference calculating step S200). Specifically, in the difference calculation step S <b> 200, information on the pressure value measured by the inlet side characteristic value measuring unit 511 is input to the first input unit 61 of the control unit 60. In the difference calculating step S <b> 200, information on the pressure value measured by the outlet side characteristic value measuring unit 521 is input to the second input unit 62 of the control unit 60. In the control unit 60, information input to the first input unit 61 and the second input unit 62 is input to the difference calculation unit 63. In the difference calculation unit 63, the difference between the pressure value on the outlet side and the pressure value on the inlet side of the compressor 50 is obtained by subtracting the information input from the first input unit 61 from the information input from the second input unit 62. Calculated.

Subsequently, in the cleaning method for the compressor 50 according to the present embodiment, it is determined whether or not the hydrate antifreeze is supplied to the internal flow path FC of the compressor 50 (hydrate antifreeze supply determination step S300). . Specifically, in the hydrate antifreeze supply determination step S300, the difference calculation unit 63 determines whether or not the hydrate antifreeze has already been supplied to the internal flow path FC. In the difference calculation part 63, when it determines with information having been once input from the 1st input part 61 and the 2nd input part 62, it determines with having already supplied the hydrate antifreezing agent to the internal flow path FC. The difference information is output to the second reference determination unit 66. Conversely, if the difference calculation unit 63 determines that no information is input from the first input unit 61 and the second input unit 62, the hydrate antifreezing agent is not supplied to the internal flow path FC. Determination is performed, and difference information is output to the first reference determination unit 64.

When it is determined that the hydrate antifreeze is not supplied to the internal flow path FC, it is determined whether or not the calculated difference satisfies a predetermined first standard (first standard determination step S400). Specifically, in the first reference determination step S <b> 400, the calculated difference is input from the difference calculation unit 63 to the first reference determination unit 64 in the control unit 60. The first reference determination unit 64 determines whether or not the input difference value is below the first reference. The first reference determination unit 64 sends a signal to the supply start instruction unit 65 when it is determined that the calculated difference is less than the first reference. Conversely, when the first reference determination unit 64 determines that the calculated difference exceeds the first reference, the first reference determination unit 64 ends the cleaning of the compressor 50 without sending a signal.

When the first reference determination unit 64 determines that the difference is less than the first reference and satisfies the first reference, the internal channel FC is supplied to the gas compressed by the compressor 50. Supply of the hydrate antifreeze is started (supply start step S500). Specifically, in the supply start step S500, the control unit 60 sends a signal from the first reference determination unit 64 to the supply start instruction unit 65, and sends a signal from the supply start instruction unit 65 to the first supply valve instruction unit 68. Sent. The first supply valve instruction unit 68 sends an instruction to the first supply valve 542 to be opened by receiving a signal from the supply start instruction unit 65. Upon receiving the instruction, the first supply valve 542 is opened, so that a part of the hydrate antifreeze flowing through the hydrate antifreeze supply unit 53 flows into the first supply pipe 541. The hydrate antifreeze that has flowed into the first supply pipe 541 is injected from the hydrate antifreeze injection unit 541a provided in the casing 501 toward the casing flow path FC2 and supplied to the internal flow path FC. . The hydrate antifreeze supplied into the internal flow path FC flows through the internal flow path FC together with the natural gas G, flows into the compressed gas flow section 52, and is discharged from the internal flow path FC.

Thereafter, the pressure value of the natural gas G is again measured and acquired at the inlet side and the outlet side of the compressor 50, and the state of the compressor 50 is measured (characteristic value acquisition step S100). Thereafter, the difference between the acquired pressure value on the inlet side and the pressure value on the outlet side of the compressor 50 is calculated (difference calculating step S200). Subsequently, it is determined whether or not a hydrate antifreeze is supplied to the internal flow path FC of the compressor 50 (hydrate antifreeze supply determination step S300). At this time, information has already been input once from the first input unit 61 and the second input unit 62. Therefore, in the hydrate antifreeze supply determination step S300, the difference calculation unit 63 determines that the hydrate antifreeze is supplied to the internal flow path FC, and outputs the difference information to the second reference determination unit 66. .

When it is determined that the hydrate antifreeze is supplied to the internal flow path FC, it is determined whether or not the calculated difference satisfies a predetermined second standard (second standard determination step S600). Specifically, in the second reference determination step S600, the control unit 60 inputs the calculated difference from the difference calculation unit 63 to the second reference determination unit 66. The second reference determination unit 66 determines whether or not the input difference value is below the second reference. The second reference determination unit 66 sends a signal to the heating supply instruction unit 67 when it is determined that the calculated difference is less than the second reference. Conversely, when the second reference determination unit 66 determines that the calculated difference exceeds the second reference, it sends a signal to the cleaning end instruction unit 70 to send the first supply valve 542 and the second supply valve 544. Is closed, and the cleaning of the compressor 50 is completed.

When the second reference determination unit 66 determines that the difference is less than the second reference and satisfies the second reference, the heated hydrate antifreeze is supplied to the internal flow path FC (heating supply step S700). ). Specifically, in the heating supply step S700, the control unit 60 sends a signal from the second reference determination unit 66 to the heating supply instruction unit 67, and the heating supply instruction unit 67 transmits the first supply valve instruction unit 68 and the second supply valve instruction unit 68. A signal is sent to the supply valve instruction unit 69. The first supply valve instructing unit 68 sends an instruction to close the first supply valve 542 by receiving a signal from the heating supply instructing unit 67. The second supply valve instructing unit 69 sends an instruction to the second supply valve 544 to be opened by receiving a signal from the heating supply instructing unit 67. When the first supply valve 542 that has received the instruction is closed, the flow of the hydrate antifreeze into the first supply pipe 541 stops. When the second supply valve 544 that has received the instruction is opened, the hydrate antifreeze starts flowing into the second supply pipe 543. The hydrate antifreeze that has flowed into the second supply pipe 543 is heated by being exchanged with the crude oil O flowing in the liquid circulation part 42 by passing through the heating part 55. The hydrate antifreeze that has been heated to a high temperature flows into the first supply pipe 541 from the downstream side of the first supply valve 542. The high temperature hydrate antifreeze flowing into the first supply pipe 541 is injected from the hydrate antifreeze injection part 541a in the casing 501 toward the casing flow path FC2 and supplied to the internal flow path FC. The high-temperature hydrate antifreeze supplied in the internal flow path FC flows through the internal flow path FC together with the natural gas G, flows into the compressed gas flow section 52, and is discharged from the internal flow path FC. .

According to the compressor system 5 as described above, the hydrate antifreeze supplied from the hydrate antifreeze supply unit 53 to the compressed gas circulation unit 52 in order to suppress the hydration of the natural gas G compressed by the compressor 50. A part of the agent is injected into the casing flow path FC2 through the first supply pipe 541 when the first supply valve 542 is opened. The hydrate antifreeze agent not only prevents the natural gas G from freezing and suppresses hydrate formation, but also has lipophilicity and hydrophilicity. Therefore, oily dirt and aqueous dirt can be removed by the hydrate antifreeze. Therefore, the hydrate antifreeze injected into the casing flow path FC2 flows in the internal flow path FC together with the natural gas G, thereby effectively removing deposits deposited on the wall surface of the internal flow path FC. Can do.
By directly supplying the hydrate antifreeze to the casing flow path FC2, the hydrate antifreeze is prevented from being diluted by the natural gas G before reaching the internal flow path FC, and the hydrate antifreeze The inside of the compressor 50 can be cleaned by effectively utilizing the above.
By utilizing a part of the hydrate antifreeze supplied from the hydrate antifreeze supply 53 to the compressed gas flow part 52, a necessary amount of hydrate antifreeze can be stably supplied to the internal flow path FC. Can be supplied.
Thus, the compressor 50 can be cleaned stably and effectively.

When the control unit 60 satisfies a predetermined condition such as the first reference determination unit 64 and the second reference determination unit 66, the hydrate antifreeze supply unit is added to the first supply pipe 541 and the second supply pipe 543. From 53, hydrate antifreeze is introduced. As a result, a hydrate antifreeze agent is ejected into the casing flow path FC2 by the hydrate antifreeze injection unit 541a. In other words, the supply control of the hydrate antifreeze to the internal flow path FC is performed by the first reference determination unit 64 and the second reference determination unit 66, so that the compressor 50 in a state that requires cleaning is limited. Hydrate antifreeze can be supplied to Therefore, the hydrate antifreeze supplied from the first supply pipe 541 and the second supply pipe 543 can be efficiently used for cleaning the compressor 50, and the supply amount of the hydrate antifreeze can be suppressed. it can.

In the control unit 60, the pressure value of the natural gas G on the inlet side of the compressor 50 measured by the inlet side characteristic value measuring unit 511 of the gas circulation unit 51 is input to the first input unit 61. In addition, in the control unit 60, the pressure value of the natural gas G on the outlet side of the compressor 50 measured by the outlet side characteristic value measuring unit 521 of the compressed gas circulation unit 52 is input to the second input unit 62. By these, the pressure value of the natural gas G at the inlet side and the outlet side of the compressor 50 can be acquired. By calculating the difference with the difference calculation unit 63 from the pressure values of the natural gas G on the inlet side and the outlet side of the acquired compressor 50, and comparing with the first reference by the first reference determination unit 64, It can be easily estimated whether or not the internal flow path FC is in a state that requires cleaning. A signal is sent from the first reference determination unit 64 to the supply start instruction unit 65 based on the determination result, and the first supply valve 542 is opened via the first supply valve instruction unit 68, so that the first supply pipe 541 is closed. The supply of the rate antifreeze can be started. As a result, injection of the hydrate antifreeze agent from the hydrate antifreeze injection unit 541a to the internal flow path FC can be started, and the internal flow path FC can be cleaned. Therefore, it can be determined with high accuracy whether or not the compressor 50 is in a state that requires cleaning, and the hydrate antifreeze can be supplied more limitedly. Accordingly, the hydrate antifreeze supplied from the first supply pipe 541 and the second supply pipe 543 is more efficiently used for cleaning the compressor 50 with respect to the internal flow path FC that requires cleaning. And the supply amount of the hydrate antifreeze can be further suppressed.

The second supply pipe 543 is provided with a heating unit 55 for heating the hydrate antifreeze. Therefore, a high temperature hydrate antifreeze can be supplied to the internal flow path FC. By being heated to a high temperature, the solubility of the hydrate antifreeze in the deposit can be improved. Therefore, the dissolution rate of the deposit accumulated in the internal flow channel FC can be improved, and the internal flow channel FC can be effectively cleaned.

The difference is calculated by the difference calculation unit 63 from the pressure values of the natural gas G at the inlet side and the outlet side of the acquired compressor 50, and the second reference determination unit 66 sets the difference larger than the first reference. By determining in comparison with the two standards, it can be easily estimated whether or not the internal flow path FC is in a state that requires cleaning again. Therefore, for example, whether the state of the internal flow path FC is different from that determined using the first reference (for example, whether more powerful cleaning is required for the internal flow path FC) is easy. Can be estimated. A signal is sent from the second reference determination unit 66 to the heating supply instruction unit 67 based on the determination result, the first supply valve 542 is closed via the first supply valve instruction unit 68, and the second supply valve instruction unit 69 is used. Then, the second supply valve 544 is opened. Thereby, the supply of the hydrate antifreeze can be started in the second supply pipe 543 provided with the heating unit 55. As a result, the hydrate antifreeze agent that has been heated to a high temperature can be injected from the hydrate antifreeze injection unit 541a to the internal flow path FC, and the internal flow path FC can be more effectively cleaned. Can do. Therefore, it can be determined with high accuracy whether or not the compressor 50 is in a state different from the case where it is determined and cleaned using the first reference, and powerful cleaning is performed on the compressor 50 as necessary. Can be implemented. Thereby, when the internal flow path FC is in a state that requires strong cleaning, the heated hydrate antifreeze can be efficiently supplied, and the compressor 50 can be cleaned more efficiently.

By using monoethylene glycol, which has a lipophilic part in the hydrocarbon part and hydrophilicity in the hydroxyl group and ether group, as a hydrate antifreeze agent, both oily dirt and aquatic dirt in the internal flow path FC are effective. Can be washed.

To wash the compressor 50 by flowing a part of the hydrate antifreeze supplied from the hydrate antifreeze supply part 53 to the compressed gas circulation part 52 through the internal flow path FC of the compressor 50 and washing it. It is not necessary to stop the operation of the compressor 50. Therefore, the compressor 50 can be efficiently cleaned without causing a cleaning down time.

According to the undersea production system 1 as described above, even the compressor 50 installed at a position where maintenance is difficult such as the seabed can be stably and efficiently washed. Therefore, clogging due to deposits can be suppressed, and the natural gas G can be stably sent onto the ship S by the compressor 50.

According to the cleaning method for the compressor 50 as described above, the difference is calculated in the difference calculation step S200 from the pressure values of the natural gas G on the inlet side and the outlet side of the compressor 50 acquired in the characteristic value acquisition step S100. In the hydrate antifreeze supply determination step S300, it is determined whether or not the hydrate antifreeze is supplied to the internal flow path FC. After that, it is possible to easily estimate whether or not the internal flow path FC is in a state requiring cleaning by making a determination in comparison with the first reference in the first reference determination step S400. Based on the determination result, the first supply valve 542 can be opened in the supply start step S500 to start the supply of the hydrate antifreeze to the first supply pipe 541. As a result, injection of the hydrate antifreeze agent from the hydrate antifreeze injection unit 541a to the internal flow path FC can be started, and the internal flow path FC can be cleaned. Therefore, it can be determined with high accuracy whether or not the compressor 50 is in a state that requires cleaning, and the hydrate antifreeze can be supplied more limitedly. Accordingly, the hydrate antifreeze supplied from the first supply pipe 541 and the second supply pipe 543 is more efficiently used for cleaning the compressor 50 with respect to the internal flow path FC that requires cleaning. And the supply amount of the hydrate antifreeze can be further suppressed.

After determining whether or not the hydrate antifreeze is supplied to the internal flow path FC in the hydrate antifreeze supply determination step S300, the first reference determination step S400 or the second reference determination step is performed based on the determination result. By performing S600, the cleaning state of the compressor 50 can be estimated. Therefore, the compressor 50 can be more efficiently cleaned according to the cleaning state of the compressor 50.

The difference is calculated in the difference calculation step S200 from the pressure values of the natural gas G on the inlet side and the outlet side of the compressor 50 acquired in the characteristic value acquisition step S100, and is larger than the first reference in the second reference determination step S600. Judgment is made by comparison with the second criterion set in the value. Thereby, it can be easily estimated whether or not the internal flow path FC is in a state that requires cleaning again. Therefore, for example, whether the state of the internal flow path FC is different from that determined using the first reference (for example, whether more powerful cleaning is required for the internal flow path FC) is easy. Can be estimated. Based on the determination result, the first supply valve 542 is closed in the heating supply step S700 and the second supply valve 544 is opened, thereby supplying the hydrate antifreeze to the second supply pipe 543 provided with the heating unit 55. Can be started. As a result, the hydrate antifreeze agent that has been heated to a high temperature can be injected from the hydrate antifreeze injection unit 541a to the internal flow path FC, and the internal flow path FC can be more effectively cleaned. Can do. Therefore, it can be determined with high accuracy whether or not the compressor 50 is in a state different from the case where it is determined and cleaned using the first reference, and powerful cleaning is performed on the compressor 50 as necessary. Can be implemented. Thereby, when the internal flow path FC is in a state that requires strong cleaning, the heated hydrate antifreeze can be efficiently supplied, and the compressor 50 can be cleaned more efficiently.

Although the embodiments of the present invention have been described in detail with reference to the drawings, the configurations and combinations of the embodiments in the embodiments are examples, and the addition and omission of configurations are within the scope not departing from the gist of the present invention. , Substitutions, and other changes are possible. Further, the present invention is not limited by the embodiments, and is limited only by the scope of the claims.

The characteristic value of the gas is not limited to the pressure value of the gas as in this embodiment, and may be a value that causes a difference in state before and after being compressed by the compressor. For example, the characteristic value of the gas may be a value obtained by measuring the temperature of the gas, a value obtained by measuring the flow rate of the gas, or a value obtained by calculating the efficiency of the compressor 50.

The internal hydrate antifreeze supply unit 54 of the present embodiment is configured to be branched into a first supply pipe 541 and a second supply pipe 543, but is not limited to such a structure, It is sufficient if the rate antifreeze agent can be supplied to the internal flow path FC of the compressor 50. For example, the internal hydrate antifreezing agent supply unit 54 may have a structure having only one of the first supply pipe 541 and the second supply pipe 543.

When determining whether the first standard or the second standard is satisfied, the hydrate antifreeze agent is not supplied based on a single determination result as in the present embodiment, but is repeated multiple times. It is good also as a structure which determines whether one standard or the 2nd standard is satisfy | filled. By setting it as such a structure, the dirt condition of the internal flow path FC can be estimated with a higher precision.

According to the above compressor system, the compressor can be efficiently cleaned by supplying the hydrate antifreeze to the internal flow path.

1 Undersea Production System S Ship F Oil and Gas Field W Production Well PF Production Fluid M Manifold FL Flow Line R Riser GR Gas Pipeline OR Oil Pipeline AR Hydrate Antifreeze Pipeline AL Umbilical Line SM Subsea Module 2 Main Heat Exchange 3 Separator 4 Pump system 41 Pump 42 Liquid flow part 43 Compressed liquid flow part 5 Compressor system 50 Compressor SL Axis line 501 Casing 502 Rotating shaft 503 Impeller 503a Disk 503b Blade 503c Cover FC Internal flow path FC1 Compression flow path FC2 Sing flow path 51 Gas flow part 511 Inlet side characteristic value measurement part 52 Compressed gas flow part 521 Outlet side characteristic value measurement part 53 Hydrate antifreeze supply part 54 Internal hydrate antifreeze supply part 541 First supply pipe 541a Hyde Rate antifreezing agent injection unit 542 First supply valve 543 Second supply pipe 544 Second supply valve 55 Heating unit 60 Control unit 61 First input unit 62 Second input unit 63 Difference calculation unit 64 First reference determination unit 65 Start of supply Instruction unit 66 Second reference determination unit 67 Heating supply instruction unit 68 First supply valve instruction unit 69 Second supply valve instruction unit 70 Cleaning end instruction unit S100 Characteristic value acquisition step S200 Difference calculation step S300 Hydray Antifreezing agent feed judging step S400 first reference determination step S500 the supply start step S600 the second reference determination step S700 heating supply step

Claims

A compressor having a casing, a rotating shaft supported in the casing, and an impeller that rotates together with the rotating shaft to compress gas;
A compressed gas flow section through which the gas compressed by the compressor flows,
A hydrate antifreeze supplying part for supplying a hydrate antifreeze to the compressed gas flow part for suppressing hydration of the gas;
A compressor comprising: an internal hydrate antifreeze supplying part for supplying a part of the hydrate antifreeze supplied by the hydrate antifreeze supplying part to an internal flow path formed by the impeller and the casing. system.
The control part which performs supply control which starts supply of the hydrate antifreeze agent to the internal channel to the internal hydrate antifreeze agent supply part when predetermined conditions are satisfied. The compressor system according to 1.
The controller is
A first reference determination unit that determines whether or not the difference between the characteristic values of the gas on the inlet side of the compressor and the outlet side of the compressor satisfies a predetermined first reference;
When the first reference determination unit determines that the first reference is satisfied, the supply of the hydrate antifreeze to the internal flow path is started with respect to the internal hydrate antifreeze supply unit. The compressor system according to claim 2, further comprising: a supply start instruction unit that sends an instruction to perform the operation.
A heating unit for heating the hydrate antifreeze,
The compressor system according to any one of claims 1 to 3, wherein the internal hydrate antifreeze supplying unit supplies the hydrate antifreeze heated by the heating unit to the internal flow path. .
A heating unit for heating the hydrate antifreeze,
The controller is
After releasing the supply of the hydrate antifreeze to the internal flow path, a difference between the gas characteristic values between the inlet side of the compressor and the outlet side of the compressor is a predetermined second value. A second reference determination unit for determining whether or not the standard is satisfied;
When it is determined that the second reference is satisfied by the second reference determination unit, the hydrate antifreeze heated by the heating unit is supplied to the internal hydrate antifreeze supply unit. The compressor system according to claim 3, further comprising a heating supply instruction unit that sends an instruction to supply the flow path.
A compressor system according to any one of claims 1 to 5;
A subsea production system comprising a separator that separates a production fluid pumped from a production well into the gas and liquid and supplies the separated fluid to the compressor.
A compressor cleaning method for cleaning a compressor having a casing, a rotating shaft supported in the casing, and an impeller that rotates together with the rotating shaft to compress gas,
A first reference determination step for determining whether or not a difference between the characteristic values of the gas on the inlet side of the compressor and the outlet side of the compressor satisfies a predetermined first reference;
When it is determined in the first reference determination step that the first reference is satisfied, the internal flow path formed by the impeller and the casing is supplied to the gas after being compressed by the compressor And a supply start step for starting supply of a hydrate antifreeze agent that suppresses the hydrate formation of the gas.
After the supply of the hydrate antifreeze agent to the internal flow path is opened, a difference between the gas characteristic value between the inlet side of the compressor and the outlet side of the compressor is a predetermined second value. A second reference determination step for determining whether or not the criterion is satisfied;
The heating supply step of supplying the heated hydrate antifreeze to the internal flow path when it is determined that the second reference is satisfied in the second reference determination step. How to clean the compressor.