JPH07324604A - Expander turbine/pump unit - Google Patents

Abstract

PURPOSE:To provide a pump suitable for pressing a self-completion liquid type that is, extremely low temperature liquefied fluid which does not require any external supply of energy. CONSTITUTION:An-expander turbine pump unit comprises a pump PU having a first discharge port 2 provided at one end of one shaft for pressurizing a liquefied fluid to a first pressure and discharging it and a second discharge port 3 for further pressurizing the liquefied fluid of the first pressure and discharging it, a heat exchanger 7 connected to the first discharge port or the second discharge port for heating and gasifying the pressurized liquefied fluid and an expander turbine ET provided at the other end of one shaft and driven by the thermal step difference obtained by reducing the pressure of the gas from the heat exchanger to a prescribed exhaust pressure.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an expander turbine / pump unit, and more particularly to liquefied natural gas (LNG).
And a pump driven by a gas turbine suitable for pumping a cryogenic liquid such as.

[0002]

2. Description of the Related Art At an LNG terminal, for example, LNG unloaded from an LNG ship is stored in an LNG tank, then discharged from the tank by an LNG pump, vaporized by a carburetor, and directly sent to a power plant for power generation. However, in the case of city gas, LPG is added to adjust the calorific value, odor is added, and the gas is delivered as city gas. The delivery pressure is about 0.5 to 0.8 MPa for power generation and 4.5 MPa for city gas.
And for city gas, the second stage LNG before vaporization
It is boosted by the pump. The LNG pump that pressurizes the cryogenic LNG is generally a multi-stage vertical centrifugal pump, and the pump and the entire motor that drives the pump are immersed in the LNG in order to eliminate the possibility of liquid leakage from the shaft seal portion. Submerged type is used (Aizawa, Kubota, "LN
Operation and Control of G Equipment ", Turbomachinery Vol. 17, No. 5, PP
8-13).

[0003]

As described above, the pump for pressurizing the LNG uses a motor to drive it, and this motor needs to be supplied with electric power of several hundred to several thousand kW. Power was supplied to this totally sealed pump from the outside through a power distribution line. However, it is difficult to manufacture a motor that requires electric power of several hundred to several thousand kW in a serve merged pump immersed in cryogenic LNG, and a facility for supplying electric power to the motor is also required. It had to be a big one. Also, from the viewpoint of energy saving, the electric power generated by the LNG at the power plant is drawn into the LNG pump in the LNG tank from the power plant through a long transmission and distribution line, and the electric power is supplied to the motor to rotate the pump. I had to do it. Therefore, to supply power to the LNG pump, loss until LNG is sent to the power plant as gas or liquid, loss of power generation efficiency at the power plant, loss at the transmission and distribution lines, loss at the time of rotating and driving the motor, etc. Was inevitably accompanied.

The present invention has been made in view of the problems of the prior art, and is a self-contained pump suitable for pressurizing and pumping a cryogenic liquid fluid that does not require external energy supply. The purpose is to provide.

[0005]

The expander turbine pump unit of the present invention is provided at one end of a single shaft,
A first discharge port for pressurizing and discharging a liquid fluid to a first pressure;
A pump having a second discharge port for further pressurizing and discharging the liquid fluid having the first pressure, and heating the pressurized liquid fluid connected to the first discharge port or the second discharge port. And a gas heat exchanger that is gasified by the heat exchanger, and an expander turbine that is provided at the other end of the one shaft and that is driven by a heat drop obtained by reducing the gas from the heat exchanger to a predetermined exhaust pressure. It is characterized by

According to a first aspect of the present invention, the liquid fluid pressurized to the first pressure is delivered from the first discharge port of the pump to the outside, and the heat exchanger is pressurized. Is a combustion heater that combusts and heats a liquid fluid to a high temperature and high pressure, and the combustion heater is connected to the second discharge port of the pump and supplies the heated gas to the expander turbine. Then, the liquid fluid is heated by burning the gas decompressed by the expander turbine by the combustion heater.

In a second aspect of the present invention, the liquid fluid pressurized to the first pressure is delivered to the outside from the first discharge port of the pump, Is a warmer that heats the liquid fluid heated by a normal temperature fluid into high-pressure gas, and is connected to the second discharge port of the pump, and supplies the heated gas to the expander turbine, It is characterized in that the gas decompressed by the panda turbine is sent to the outside as high-pressure gas.

In a third aspect of the present invention, the liquid fluid pressurized to the second pressure is delivered to the outside from the second outlet of the pump, and the heat exchanger is pressurized to the outside. Is a combustion heater that combusts and heats a liquid fluid to a high temperature and high pressure, and is connected to the first outlet of the pump, and supplies the heated gas to the expander turbine to expand the expander. It is characterized in that the liquid fluid is heated by burning gas decompressed by a turbine by the combustion heater.

In a fourth aspect of the present invention, the liquid fluid pressurized to the second pressure is delivered to the outside from the second discharge port of the pump, and the heat exchanger applies the pressure to the pressure. Is a warmer that heats the liquid fluid heated by a normal temperature fluid to gasify it at high pressure, is connected to the first discharge port of the pump, and supplies the heated gas to the expander turbine, It is characterized in that the gas decompressed by the panda turbine is sent to the outside as high-pressure gas.

[0010]

The pump of the present invention has the first discharge port and the second discharge port as described above. Therefore, while pressurizing the liquid fluid to a predetermined pressure from one of the discharge ports and delivering it,
The expander turbine is connected to the other discharge port by connecting a heat exchanger that heats the pressurized liquid fluid to gasify it, and reduces the high-pressure gas from the heat exchanger to a predetermined exhaust pressure to obtain a heat drop. The pump can be rotated by driving. The gas obtained by driving the expander turbine to reduce the exhaust pressure to a specified level can be sent as city gas or power generation gas, and can also be burned by a combustion heater and used to heat the liquid fluid. You can also In this way, the expander turbine of the present invention
According to the pump unit, the pump can be rotationally driven by its own liquid to pressurize the liquid fluid to a predetermined pressure and send it out without receiving supply of electric energy or the like from the outside.

[0011]

Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is an explanatory diagram of a system system of an expander turbine pump unit according to the first and third embodiments of the present invention. FIG. 2 is an explanatory diagram of a system system of the expander turbine pump unit according to the second and fourth embodiments of the present invention. 3 is a sectional view of a pump unit according to the first and second embodiments of the present invention, and FIG. 4 is a sectional view of a pump unit according to the third and fourth embodiments of the present invention. FIG. 5 is a pressure-enthalpy line showing the thermodynamic state of the liquid fluid in the expander turbine pump unit of the first and second embodiments of the present invention, and FIG. 6 is the third and fourth embodiments of the present invention. It is a figure. still,
In the drawings, the same reference numerals indicate the same or corresponding parts.

The vertically arranged drive shaft DS of the pump, which is generally designated by the symbol PU, is designated by the symbol E at its upper part.
It is connected to the main shaft of the expander turbine indicated by T. The drive shaft DS is one main shaft that penetrates the pump PU and the expander turbine ET, but the main shafts of the pump and the turbine may be connected to each other. The casings of the pump PU and the turbine ET are connected to each other by a connecting pipe 21 having a main axis direction thermal deformation absorber, that is, a bellows portion 21a. The discharge port 2 of the pump PU is a first-stage discharge port that pressurizes the liquid fluid to a predetermined pressure and sends it to the outside. The discharge port 3 is a second-stage discharge port that further pressurizes and discharges the remaining liquid fluid of the liquid fluid delivered from the discharge port 2. The expander turbine ET is provided with an air supply port 5 and an exhaust port 6
The turbine is a turbine that rotates an impeller by expanding the high-pressure gas sucked from the exhaust gas, and the expanded and depressurized gas is discharged from the exhaust port 6. The combustion heater 7 in FIG. 1 is a heat exchanger that heats a pressurized liquid fluid into a high-temperature and high-pressure gas state. The combustion heater 7 uses a gasified liquid fluid as a fuel and applies heat generated by combustion to the pressurized liquid fluid to gasify the liquid fluid at high temperature and high pressure. In this embodiment, the cryogenic liquid fluid flowing into the combustion heater 7 is, for example, a high temperature gas of about 500 ° K. In addition, the warmer 8 in FIG. 2 heats the liquid fluid pressurized from the cryogenic pump PU flowing from the inlet 8A to normal temperature (300 ° K) to high pressure gas, and then from the outlet 8D. It is a heat exchanger that discharges. For example, heat exchange is performed while a heat exchange medium at room temperature, such as seawater, flows in through the inlet 8C and flows out through the outlet 8D.

Next, the system system and operation of the expander turbine pump unit of the first embodiment of the present invention will be described with reference to FIG. The re-pressurized liquid fluid discharge port 3 and the air supply port 5 of the expander turbine ET are connected by a line L, and the line L is provided with a combustion heater 7. A flow rate adjusting valve V1 is provided in the middle of the line L, the valve V1 is connected to a controller CU, and the rotation sensor 29 of the drive shaft DS is connected to the controller CU. The outlet 7B of the gasified liquid fluid of the combustion heater 7 is connected to the turbine ET.
Of the turbine ET is connected to the burner BU of the combustion heater 7 through the exhaust port 6 of the turbine ET. The upstream side of the valve V1 of the line L is connected to the liquid fluid delivery line 9 via the flow rate adjusting valve V2 connected to the controller CU by the line L1, and the opening of the connecting pipe 21 is the line L.
2 is connected to the exhaust port 6 of the expander turbine ET. If necessary, an orifice may be inserted in the line L2. Further, the line L is connected to a starting line L3 from a primary pump (not shown) or the like, and an excess gas line L4 that can be used for starting is connected to the upstream side of the air supply port 5 of the turbine ET.

Therefore, the liquid fluid W sucked into the pump PU from the suction port 1 by a primary pump (not shown)
Is pressurized to a predetermined pressure and is delivered to the outside from the delivery pipe 9 as a liquid fluid pressurized from the first discharge port 2.
For example, if the liquid fluid is LNG, it is sent in a liquid pressurized state to another LNG base via a pipeline. The liquid fluid further pressurized from the second discharge port 3 of the pump PU passes through the flow rate adjusting valve V1 and the line L and enters the combustion heater 7 through its inlet 7A. The liquid fluid pushed into the combustion heater 7 from the inlet 7A is heated and becomes a high-temperature and high-pressure gas, which is the air supply port 5 of the expander turbine ET.
Flow into the turbine, expand and rotate the impeller of the turbine, and the gas becomes decompressed. The combustion heater 7 is supplied with a gas (for example, a fuel gas such as LNG) whose pressure is reduced from the exhaust port 6 of the expander turbine and combusts the same to thereby combust and heat the liquid fluid flowing from the line L. The exhaust gas burned in the combustor BU is exhausted from the line L _EX .

Since this pump unit does not have a function of starting itself, at the time of start-up, high pressure gas is sent from the air supply port 5 through the line L3 or L4 to start the turbine ET or ignite the burner BU. If you gradually rotate the pump PU and raise it to a predetermined speed,
The energy balance is established, and the number of revolutions increases automatically until the balance is reached. The rotation speed is detected by the rotation sensor 29, and the controller CU controls the flow rate adjusting valve V.
The amount of inflow to the combustion heater 7 can be adjusted by 1 and V2 to control the rotation speed. Further, the rotational speed can be similarly controlled by adjusting the flow rate of the combustion gas or the combustion temperature in the burner BU. Further, a generator can be directly connected to the main shaft of the turbine ET to generate electricity with surplus energy.

As described above, the present pump unit can pressurize the liquid fluid and use it in a liquid state for long-distance transportation and the like, and further repressurize a part of the liquid fluid to gasify it by heating. By expanding, the impeller of the expander turbine can be rotated, and the pump directly connected to the main shaft of the turbine can be rotationally driven. The heating can be performed by burning the exhaust gas that drives the turbine.

FIG. 3 shows the structure of the pump unit of this embodiment. The expander turbine ET is provided on the pump cover 17 of the pump PU. These pumps P
The common drive shaft DS of U and the turbine ET is an upper portion composed of a thrust bearing 12 and a radial bearing 13 formed of non-contact magnetic bearings on the turbine ET side and a magnetic bearing or a low pressure bearing on the pump PU side in order from above. It is supported by a bearing 19 and a lower bearing 20. In the figure, reference numeral 14 is a non-contact type labyrinth seal, reference numeral 1 is a suction port of the pump, 2 is a first discharge port of the pump, and 3 is a second discharge port. The liquid fluid flowing in from the suction port 1 of the pump is the upper impeller 23.
And is branched in the intermediate chamber 25, one of which is sent to the outside through the first discharge port 2 and the remaining pressurized liquid fluid is further repressurized by the lower impeller 28 and discharged. It is sent out from the outlet 3.

Next, a second embodiment of the present invention will be described with reference to FIG. In the present embodiment, the combustion heater 7 is used as the heat exchanger in the first embodiment, whereas the warmer 8 using a fluid such as normal temperature seawater is used as the heat exchange medium. Therefore, the cryogenic pressurized fluid flowing in from the inlet 8A of the warmer 8 becomes a high-pressure gas body heated to about room temperature (300 ° K) at its outlet 8B.
Then, this high-pressure gas is sucked into the air supply port 5 of the turbine ET through the line L, expands, rotationally drives the impeller of the turbine, and the depressurized gas is discharged from the exhaust port 6 of the turbine ET to a high pressure gas of a predetermined pressure. As an external line. The other system system is the same as that of the first embodiment shown in FIG. 1, and the structure of the pump is also the same as that of the first embodiment shown in FIG.

The pump unit of the present embodiment is suitable for a case where it is installed at an LNG base and locally generates electricity with gas (LNG) while delivering it with liquid (LNG) for long-distance transportation. In this case, when the discharge pressure of the pump is too high with respect to the required delivery pressure, the power recovery turbine can reduce the pressure to the required pressure to recover energy.

Next, a third embodiment of the present invention will be described with reference to FIGS.
A fourth embodiment will be described with reference to FIGS. 2 and 4. In the first and second embodiments of the present invention described above, the first discharge port of the pump is used to deliver the liquid fluid to the outside, and the second discharge port is connected to the heat exchanger to repressurize the liquid. While the fluid is heated and gasified, in the third and fourth embodiments, the second outlet of the repressurized liquid fluid of the pump is connected to the pressurized liquid delivery line to the outside, and the intermediate The first outlet of the stage is connected to a heat exchanger. Here, as the heat exchanger, the heating combustor 7 is used in the third embodiment, and the warmer 8 which is heated by the normal temperature fluid is used in the fourth embodiment. FIG. 4 shows the structure of the pump of this embodiment, which is provided with an upper impeller 23 for pressurizing the suction port 1 to a predetermined pressure, a first discharge port 2'that discharges at a predetermined pressure, and the remaining liquid. A second discharge port 3 ′ is provided for repressurizing the fluid by the lower impeller 28 and discharging the fluid. In the system configuration of the third embodiment, the first discharge port 2'of the intermediate stage of the pump PU is connected to the inlet 7A of the combustion heater 7, and the repressurized second discharge port 3'of the pump PU is exposed to the outside. Is connected to the sending line 9 of.
Further, in the system configuration of the fourth embodiment, the first discharge port 2'of the intermediate stage of the pump PU is connected to the inlet 8A of the heater 8 for the normal temperature fluid, and the repressurized second discharge port of the pump PU is connected. 3'is connected to the outgoing line 9 to the outside.

According to the third and fourth embodiments, the pressure applied to the liquid can be increased when the liquid is sent out for long-distance transportation, and the liquid taken out from the intermediate stage is gasified by heat exchange. By rotating the expander turbine, the pump can be driven by its own liquid. Further, the gas expanded and decompressed by the turbine ET is used as a combustion gas for heating a liquid fluid in the third embodiment, and can be sent to the outside for power generation or city gas in the fourth embodiment. .

Next, the operating principle of the expander turbine pump unit of the first and second embodiments of the present invention will be described with reference to FIG. The cryogenic fluid such as LNG or liquid hydrogen is pressurized from the state S ₀ near atmospheric pressure P ₀ to the pressure P ₁ by the primary pump in the state S _0.
Becomes ₁ . Then, the pump PU of the present embodiment, which is a secondary pump, pressurizes to a pressure P _{2 in} a polytropic manner in consideration of the loss, and discharges most of the liquid fluid from the discharge port 2. The remaining liquid fluid further pressurized to the pressure P ₃ reaches the state S ₃ . Here, the heat quantity of the combustion heater 7 in the first embodiment and the heat exchanger of the warmer 8 in the second embodiment receive the heat quantity, and the state moves to the state S ₄ where the pressure is low by the loss of the heat exchanger.
Polytropic expansion is performed from this state S ₄ to a state S ₅ which is deviated by a turbine loss on the line with constant entropy.
Then, ahead of this, in the first embodiment, the pressure goes toward the state S ₆ side (combustion) due to a constant pressure change in the combustion heater burner BU. In the second embodiment, a high pressure gas having a pressure of P ₅ is delivered to the outside.

The expander turbine / pump unit is intended to drive the expander turbine by utilizing the difference in gradient between the isentropic line in the supersaturated liquid range and the isentropic line in the superheated state. This means that the enthalpies of the states S ₁ , S ₂ , S ₃ , S ₄ , and S ₅ are i ₁ , i ₂ , i ₃ , i ₄ , and i ₅ , respectively, and the total inflow amount W of the pump is W.
If W (i ₂ −i ₁ ) + w (i ₃ −i ₂ ) ≦ w (i ₄ −i ₅ ), where kg is the extracted amount wkg, then the system is valid. _{That, W (i 2 -i 1)} ≦ w (i 4 -i 5 -i 3 + i 2) w / W ≧ (i 2 -i 1) / (i 4 -i 5 + i 2 -i 3) That is, It is sufficient that (i ₂ −i ₁ ) / (i ₄ −i ₅ + i ₂ −i ₃ ) is 1 or less. The states S ₃ and S ₄ may be set so that the above equation for supplying the heated gas to the expander turbine and sending the exhaust gas of the expander turbine as high-pressure gas to the outside is satisfied. To do this, change the pressure P ₃ and increase the amount of entropy i ₄ due to heat input.
Two degrees of freedom are conceivable, that is, -i ₃ is adjusted. Further, the quantity w (i ₄ −i ₅ ) is the quantity W (i ₂ −i ₁ ) + w (i
When it is sufficiently larger than _3- i ₂ ), a part can be used for driving the pump and the rest can be used for power generation. At that time, although it is necessary to adjust the frequency, a generator can be attached to the shaft end of the expander turbine to generate electric power.

Here, the establishment of the above system will be quantitatively explained by taking liquid hydrogen as an example.

Here, the saturation pressure P ₀ = 0.1 at 21 ° K.
2 MPa, i ₀ = 270 kJ / kg of liquid hydrogen, P ₅ =
Consider the case of burning as a gas of 0.5 MPa. The primary pump raises the pressure to P ₁ = 0.28 MPa, and further, the secondary pump pressurizes the pressure to P ₂ . The partially extracted liquid was repressurized to P ₃ = 10 MPa, and the temperature was raised to 500 ° K by a heat exchanger (combustion heater) having a loss of 1.5 MPa, and then it was adjusted to 0. Suppose to expand to 5 MPa. First, assuming that the state corresponding to the state S ₁ is isentropic change, P ₁ = 0.28 MPa, i _1s = 272 kJ / kg,
Assuming that the pump efficiency ηp is 60%, i ₁ = (i _1s −i ₀ ) / ηp + i ₀ = (272-270) /
0.60 + 270 = 273 kJ / kg Next, in the state S ₂ , P ₂ = 7.5 MPa i ₂ = (i _2s −i ₁ ) / ηp + i ₁ = (370−27
3) /0.6+273=434 kJ / kg Further pressurizing the partially extracted liquid to P ₃ = 10 MPa,
Assuming the state of S ₃ , i _3S = 470 kJ / kg i ₃ = (i _3s −i ₂ ) / ηp + i ₂ = (470−43
4) /0.6+434=494 kJ / kg T = 500 ° K, i ₄ = 7180 kJ /
If the kg expander total adiabatic efficiency ηe = 70%, then i _5s = 3030 kJ / kg if it isentropically reduced to P ₅ = 0.5 MPa i ₄ −i ₅ = (i ₄ −i _5s ) * ηe = (7180-3
030) * 0.7 = 2905kJ / kg _{Therefore, (i 2 -i 1) /} (i 4 -i 5 + i 2 -i 3) = (434-273) / (2905 + 434-494) = 0.0566 Thus It can be seen that the pump can be driven sufficiently. That is, the pressure P ₃ or the temperature T may be lower. From the same calculation, it can be seen that even in the case of liquid methane, which is the main component of LNG, the pump can be driven by appropriately selecting the pressure P ₃ .

FIG. 6 is a pressure-enthalpy diagram of the expander turbine pump unit of the third and fourth embodiments. Similar to FIG. 5, the cryogenic fluid such as LNG or liquid hydrogen is pressurized from the state S ₀ near the atmospheric pressure P ₀ to the pressure P ₁ by the primary pump to be the state S ₁ .
Then, the pump PU of the present embodiment, which is a secondary pump
Is polytropically pressurized to a pressure P ₃ in consideration of the loss, and a part of the liquid fluid wkg is delivered from the discharge port 2 ′ to the heat exchangers 7 and 8. Furthermore, the remaining liquid fluid (W-w)
kg is pressurized to a pressure P _2, reaches state S _2. Then, the liquid fluid that has reached the state S ₂ is sent to the external pipeline. The liquid fluid wkg extracted in the state S ₃ is
Combustion heater 7 in the third embodiment, warmer 8 in the fourth embodiment.
The heat quantity is received by the heat exchanger, and the state moves to the state S ₄ where the pressure is low by the loss of the heat exchanger. Polytropic expansion is performed from this state S ₄ to a state S ₅ which is deviated by a turbine loss on the line with constant entropy. Then, in the third embodiment, the tip moves toward the state S ₆ (combustion) due to the equal pressure change in the burner BU of the combustion heater. In the fourth embodiment,
It is delivered to the outside as a high-pressure gas having a pressure of P ₅ . Therefore, as in FIG. 5, W (i ₃ −i ₁ ) + (W−w) (i ₂ −i ₃ ) ≦ w (i
_{If 4-} i ₁ ), then the system holds. That is, w / W ≧ (i ₂ −i ₁ ) / (i ₄ −i ₅ + i ₂ −i ₃ ).

The establishment of this system will be quantitatively examined using liquid hydrogen as an example. Similar to the above, consider a case where liquid hydrogen having a saturation pressure of 21 ° K P ₀ = 0.12 MPa and i ₀ = 270 kJ / kg is burned as a gas of P ₅ = 0.5 MPa. P ₁ = 0.28 by the primary pump
The pressure is increased to MPa and the pressure P ₃ = with the secondary pump.
Pressurize to 4 MPa. 1.5MP for partially extracted liquid
After raising the temperature to 500 ° K with a heat exchanger (combustion heater) having a loss of a, 0.5 with an expander turbine.
Suppose to expand to MPa. First, if the state corresponding to the state S ₁ is an isentropic change, P ₁ = 0.28M
Pa, i _1s = 272 kJ / kg, pump efficiency ηp is 60
%, I ₁ = (i _1s −i ₀ ) / ηp + i ₀ = (272-270) /
0.60 + 270 = 273 kJ / kg Next, in the state S ₃ , P ₃ = 4 MPa i ₃ = (i _3s −i ₁ ) / ηp + i ₁ = (326−27
3) /0.6+273=361 kJ / kg Further, if the partially extracted liquid is heated to T = 500 ° K, i ₄ = 7120 J / kg and P ₂ = 7.5 MPa, i _2s = 410 kJ / kg. i ₂ = i ₃ + (i _2s −i ₃ ) / ηp = 361 + (410−
361) /0.6=443 kJ / kg Expander Total adiabatic efficiency ηe = 70%, i ₄ −i ₅ = (i ₄ −i _5s ) * with isentropic drop to P ₅ = 0.5 MPa ηe = (7120-4
500) * 0.7 = 1834kJ / kg _{Therefore, (i 2 -i 1) /} (i 4 -i 5 + i 2 -i 3) = (443-273) / (1834 + 443-361) = 0.088 Thus In addition, it can be seen that the pumps can be sufficiently driven also in the third and fourth embodiments.

FIG. 7 shows another embodiment of the present invention. In this embodiment, the drive shaft DSA is a horizontal shaft, and a pump PUA and an expander turbine DTA are provided at both ends of the drive shaft DSA, respectively. Pump PUA
The turbine DTA and the turbine DTA are connected by a connecting cylinder 21 which is a connecting portion, and the recovery casing 21 is provided below the connecting cylinder 21A.
B is provided. Reference numeral 10A in the figure is a pump PU
A non-contact type shaft seal that allows the liquid leakage on the A side to some extent, and a reference numeral 4A is a non-contact type labyrinth seal on the turbine DTA side. Pump PUA and turbine DTA
The configuration of is the same as the pump PU and the turbine ET shown in FIGS. 1 to 4 except that they are of the horizontal axis type.

In the figure, the liquid flow is shown by a solid line, the gas flow is shown by a chain line, the thick line shows the main flow, and the thin line shows the leakage. The liquid is pumped from the suction port 1 in the state S1 to the pump PUA.
It enters the inside, is pressurized to a predetermined pressure, becomes the state S2, and is delivered to the outside from the discharge port 2. A part of the liquid is further pressurized and discharged from the discharge port 3 in the state S3. The liquid discharged from the discharge port 3 enters the combustion heater 7 and is heated to a state S4, flows into the turbine DTA from the suction port 5 and is decompressed to a state S5 and is discharged from the exhaust port 6 to burn. It is sent to the burner BU of the heater 7 and burned.

The pressure in the connecting cylinder 21 is set by the arrangement of the number of stages of the pump PUA as in the embodiment shown in FIGS. 1 and 2.
It is basically equal to the discharge pressure of the expander turbine DTA in state S5 and is kept at a slightly higher value. The leakage to the turbine DTA to the connecting cylinder 21 comes out through the non-contact labyrinth seal 4A, but the inside of the connecting cylinder 21 has a pressure difference of about the head of the turbine DTA. On the other hand,
There is basically no differential pressure in the shaft penetrating portion on the pump PUA side,
Even if there is a differential pressure, it is very small, and leakage prevention at this portion can be performed by allowing a certain amount of leakage with a non-contact shaft seal 10A similar to a mechanical seal, a floating ring, or the like. A seal mechanism that allows such leakage to some extent maintains a desired life as an industrial machine. As described above, the pressure inside the coupling cylinder 21A is basically the same as the discharge pressure state S5 of the turbine as described above, so that the leakage gas from the turbine DTA and the pump P
The gas generated when leaking from the UA can be injected from the opening N into the gas delivery line that is the outlet of the turbine DTA. Also, the liquid leaked from the pump PUA is
Can be recovered in the lower drain recovery casing 21B, injected into the combustion heater 7 by a small recovery pump, gasified, and injected into the delivery line.

The horizontal axis type pump PUA and turbine E
In the TA configuration, the combustion heater 7 may be replaced with the warmer 8 according to the second embodiment of the present invention described above. Further, according to the third embodiment of the present invention, the discharge port of the intermediate stage of the pump PUA is connected to the combustion heater 7 so that the liquid is discharged from the discharge port of the repressurized liquid to the outside. Good. Furthermore, according to the fourth embodiment of the present invention, the discharge port of the intermediate stage of the pump may be connected to the warmer 8 so that the repressurized liquid is discharged to the outside. .

In the above description of the embodiments, liquid hydrogen and LNG are used as the liquid to be pressurized by the pump, but it goes without saying that other low temperature fluids such as liquid nitrogen can be applied. is there. Further, the example in which the discharge port of the pump has two stages has been described, but it may have three stages or four stages because of the necessity of the entire system configuration. Further, it goes without saying that the configuration of the connecting portion of the horizontal shaft type pump of FIG. 7, that is, the configuration including the non-contact type shaft seal for preventing liquid leakage on the pump side can be applied to the hard shaft type pump shown in FIGS. 3 to 4, for example. It is possible.

[0033]

As described above, in the expander turbine / pump unit of the present invention, the pump has the two-stage discharge port, and the liquid pressurized from one of the discharge ports is heat-exchanged for gasification. By doing so, the expander turbine can be driven and pressurized liquid can be sent from the discharge port of the other pump. Therefore, it is possible to configure a self-contained pump that does not require the supply of an energy source from the outside. Therefore, such a pump contributes to energy conservation and maintenance of a clean environment by being used in an LNG base or the like.

[Brief description of drawings]

FIG. 1 is an explanatory diagram showing a system system of an expander turbine pump unit according to first and third embodiments of the present invention.

FIG. 2 is an explanatory diagram showing a system system of an expander turbine / pump unit according to second and fourth embodiments of the present invention.

FIG. 3 is a partial cross-sectional front view showing the configuration of the pumps according to the first and second embodiments of the present invention.

FIG. 4 is a partial cross-sectional front view showing the configurations of pumps according to third and fourth embodiments of the present invention.

FIG. 5 is a pressure-enthalpy diagram showing the thermodynamic state of the liquid fluid in the expander turbine pump unit of the first and second embodiments of the present invention.

FIG. 6 is a pressure-enthalpy diagram showing the thermodynamic state of the liquid fluid in the expander turbine / pump unit of the third and fourth embodiments of the present invention.

FIG. 7 is an explanatory diagram showing a system system of a horizontal axis type expander turbine pump unit according to another embodiment of the present invention.

[Explanation of symbols]

 PU, PUA Pump DT, DTA Expander Turbine 1 Pump suction port 2 Pump first discharge port 3 Pump second discharge port 5 Turbine air inlet port 6 Turbine exhaust port 7 Combustion heater 8 Heater 9 Liquid fluid delivery line 21 Connection cylinder

Claims (6)

[Claims] 1. A first discharge port which is provided at one end of a uniaxial shaft and pressurizes and discharges a liquid fluid at a first pressure, and a second discharge port which further pressurizes and discharges the liquid fluid at the first pressure. A pump having an outlet, a heat exchanger connected to the first discharge port or the second discharge port to heat and gasify the pressurized liquid fluid, and the heat exchanger provided at the other end of the one shaft. An expander turbine / pump unit comprising an expander turbine driven by a heat drop obtained by reducing the gas from the heat exchanger to a predetermined exhaust pressure. 2. The liquid fluid pressurized to the first pressure is delivered to the outside from the first discharge port of the pump, and the heat exchanger burns and heats the pressurized liquid fluid. Is a combustion heater that gasifies to high temperature and high pressure, the combustion heater is connected to the second discharge port of the pump, the heated gas is supplied to the expander turbine, The expander turbine / pump unit according to claim 1, wherein the liquid fluid is heated by burning the depressurized gas in the combustion heater. 3. The liquid fluid pressurized to the first pressure is delivered to the outside from the first discharge port of the pump, and the heat exchanger supplies the fluid liquid pressurized to the room temperature fluid. Is a warmer for heating to high pressure gas by means of a heater, the warmer being connected to the second discharge port of the pump, and supplying heated gas to the expander turbine, The expander turbine / pump unit according to claim 1, wherein the gas decompressed by the above is sent to the outside as a high pressure gas. 4. The liquid fluid pressurized to the second pressure is delivered to the outside from the second discharge port of the pump, and the heat exchanger burns and heats the pressurized liquid fluid. Is a combustion heater that gasifies to high temperature and high pressure, is connected to the first discharge port of the pump, supplies the heated gas to the expander turbine, the gas decompressed by the expander turbine is The expander turbine pump unit according to claim 1, wherein the liquid fluid is heated by being burned by a combustion heater. 5. The liquid fluid pressurized to the second pressure is delivered to the outside from the second discharge port of the pump, and the heat exchanger transfers the pressurized liquid fluid to a normal temperature fluid. Is a warmer that is heated by means of a high pressure gas, is connected to the first discharge port of the pump, the heated gas is supplied to the expander turbine, the gas decompressed by the expander turbine The expander turbine pump unit according to claim 1, wherein the expander turbine pump unit is delivered as high-pressure gas to the outside. 6. The shaft of the pump and the expander turbine is connected so as to cover the one shaft to form a closed structure, and a non-contact shaft is provided in a penetrating portion of the pump and the expander turbine of the one shaft. The expander turbine pump unit according to claim 1, further comprising a pipe provided with a seal, and the liquid fluid and the gas leaked by the shaft seal are collected and reused.