JP2014214896A - Supercritical pressure fluid heat exchanger and power generation system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of reducing pressure loss and improving heat exchange amount.SOLUTION: A supercritical pressure fluid heat exchanger according to the present embodiment implements heat exchange between a low boiling point medium at a supercritical pressure lower in boiling point than water and a heat source medium to heat the low boiling point medium at the supercritical pressure. The supercritical pressure fluid heat exchanger according to the present embodiment comprises: a plurality of heat transfer tubes; a body; and a plurality of baffles. The heat source medium flows in the plurality of heat transfer tubes. The body accommodates therein the plurality of heat transfer tubes and the low boiling point medium at the supercritical pressure flows around the plurality of heat transfer tubes. The plurality of baffles are disposed aligned with one another at intervals within the body so that the low boiling point medium at the supercritical pressure can flow from an inlet to an outlet in a meandering manner. The plurality of baffles are disposed so that a distance between one baffle and the other baffle disposed adjacent to one baffle is longer along a flow of the low boiling point medium at the supercritical pressure within the body.

Description

  Embodiments described herein relate generally to a supercritical fluid heat exchanger and a power generation system.

  2. Description of the Related Art There is known a power generation system that generates power by heating a working medium using heat such as geothermal heat, biomass heat, and ironworks waste heat.

  In such a power generation system, since the temperature of the heat source for heating the working medium is relatively low, a low boiling point medium having a boiling point lower than that of water may be used as the working medium. For example, fluorocarbons such as hydrofluorocarbon (HFC) and organic media such as hydrocarbons such as butane and pentane are used as the low boiling point media (see, for example, Patent Documents 1 to 7).

JP 2009-221961 US Patent No. 5400598 US Pat. U.S. Patent No. 6009711 U.S. Patent No. 7775045 US Patent No. 7797940 U.S. Patent No. 7823386

  In the above power generation system (organic medium Rankine cycle (ORC) power generation system), in order to increase the efficiency of power generation, the low boiling point medium is boosted to the supercritical pressure, and then the low boiling point medium with the supercritical pressure is used as the heat source medium. It is heated by heat exchange and supplied to the turbine.

  The heat exchange between a supercritical pressure low boiling point medium and a heat source medium is, for example, a multi-tube type (shell and tube type) heat exchange in which multiple heat transfer tubes (tubes) are arranged inside a shell (shell). In the vessel. In a multi-tube heat exchanger, cleaning is easier in the heat transfer tube than in the body. For this reason, when the cleanliness of the heat source medium is poor, the heat source medium is caused to flow inside the heat transfer tube, and the low boiling point medium having a supercritical pressure is caused to flow around the heat transfer tube inside the trunk, thereby Exchange is performed.

FIG. 11 is a diagram showing the relationship between temperature and specific heat and the relationship between temperature and density for a supercritical fluid. In FIG. 11, the horizontal axis indicates the temperature T (° C.), the left vertical axis indicates the constant pressure specific heat Cp (J / kg / K), and the right vertical axis indicates the density ρ (kg / m ³ ). Yes.

  As shown in FIG. 11, the constant pressure specific heat Cp of the supercritical pressure fluid increases as the temperature T increases. Here, when the supercritical fluid becomes near the critical temperature TC, the constant pressure specific heat Cp increases rapidly. When the supercritical pressure fluid reaches the pseudocritical temperature TE, the constant pressure specific heat Cp becomes maximum. When the supercritical pressure fluid is further heated and exceeds the pseudocritical temperature TE, the constant pressure specific heat Cp decreases and becomes substantially the same as the constant pressure specific heat Cp in a temperature range lower than the critical temperature TC.

  In addition, as the temperature T increases, the density ρ of the supercritical fluid decreases. Here, when the supercritical pressure fluid exceeds the vicinity of the critical temperature TC, the density ρ decreases rapidly, and the density is about 1/4 to 1/6 of the density ρ when the fluid is lower than the critical temperature TC. becomes ρ.

  For this reason, the low-boiling-point medium having a supercritical pressure may rapidly increase in flow rate inside the cylinder. And pressure loss may increase with the increase in the flow velocity. In addition, as the constant pressure specific heat Cp increases, the temperature difference between the low boiling point medium and the heat source medium decreases, and the heat exchange amount may decrease.

  As a result, it may not be easy to achieve sufficient efficiency for the power generation system.

  Therefore, the problem to be solved by the present invention is to provide a heat exchanger capable of reducing pressure loss and improving the amount of heat exchange, and a power generation system capable of realizing efficiency.

  In the supercritical fluid heat exchanger of the present embodiment, heat exchange is performed between a low-boiling medium having a supercritical pressure having a boiling point lower than that of water and a heat source medium, and the low-boiling medium having a supercritical pressure is heated. The supercritical fluid heat exchanger according to the present embodiment includes a plurality of heat transfer tubes, a trunk, and a plurality of baffle plates. In the plurality of heat transfer tubes, the heat source medium flows inside. The cylinder accommodates a plurality of heat transfer tubes therein, and a supercritical low-boiling-point medium flows around the plurality of heat transfer tubes. The plurality of baffle plates are arranged side by side in the cylinder so that a low-boiling medium having a supercritical pressure flows meandering from the inlet toward the outlet in the cylinder. Here, the plurality of baffle plates are such that the distance between one baffle plate and another baffle plate installed next to the one baffle plate is the low-boiling-point medium having the supercritical pressure inside the trunk. It is installed so that it may become long along the flow.

FIG. 1 is a system diagram showing a power generation system according to the first embodiment. FIG. 2 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the first embodiment. FIG. 3 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the first embodiment. FIG. 4 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the first embodiment. FIG. 5 is a cross-sectional view showing in detail the arrangement of the plurality of baffle plates 25 in the supercritical fluid heat exchanger 2 of the power generation system according to the first embodiment. FIG. 6 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the second embodiment. FIG. 7 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the second embodiment. FIG. 8 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the second embodiment. FIG. 9 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the third embodiment. FIG. 10 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the fourth embodiment. FIG. 11 is a diagram showing the relationship between temperature and specific heat and the relationship between temperature and density for a supercritical fluid.

  Embodiments will be described with reference to the drawings.

<First Embodiment>
[A] Configuration of Power Generation System FIG. 1 is a system diagram showing a power generation system according to the first embodiment.

  In the present embodiment, the power generation system is an ORC power generation system, and as shown in FIG. 1, a supercritical pressure fluid heat exchanger 2, a medium turbine 3, a condenser 4, and a supercritical pressure medium pump 5 And a cooling water supply unit 6.

  Below, each part which comprises a power generation system is demonstrated sequentially.

[A-1] Supercritical fluid heat exchanger 2
As shown in FIG. 1, the supercritical fluid heat exchanger 2 uses a heat source medium F1 supplied from the heat source medium supply source 1 to heat a low boiling point medium M5 having a lower boiling point than water. . The supercritical fluid heat exchanger 2 is an evaporator, and heats the low-boiling point medium M5 having a supercritical pressure to a temperature higher than the critical temperature TC and the pseudocritical temperature TE to form a supercritical gas fluid.

  Specifically, the supercritical fluid heat exchanger 2 is provided with a pipe between the heat source medium supply source 1 and the heat source medium F1 is used as a heating medium via the pipe. Inflow. For example, the heat source medium supply source 1 is a production well (not shown) for supplying geothermal water heated by geothermal heat, and the geothermal water from the production well serves as a heat source medium F1 as a supercritical pressure fluid heat exchanger. It flows into 2 and enters the inside. In addition, the heat source medium F1 may be a medium heated by heat such as heat from biomass resources or waste heat from a steel mill in addition to geothermal heat.

  At the same time, the supercritical pressure fluid heat exchanger 2 is provided with a pipe between the supercritical pressure medium pump 5 and the pressure is raised to the supercritical pressure by the supercritical pressure medium pump 5 through the pipe. The low boiling point medium M5 flows in. For example, the low boiling point medium M5 is an organic medium such as Freon (hydrofluorocarbon (HFC), hydrofluoroolefin (HFO), etc.), hydrocarbon (butane, pentane, etc.).

  Then, in the supercritical pressure fluid heat exchanger 2, heat exchange is performed between the heat source medium F1 and the supercritical pressure low boiling point medium M5.

  In the supercritical fluid heat exchanger 2, the heat source medium F1 is cooled by heat exchange with the low boiling point medium M5 having a supercritical pressure. And the heat source medium F2 after heat exchange is discharged | emitted from the supercritical pressure fluid heat exchanger 2 outside.

  On the other hand, in the supercritical fluid heat exchanger 2, the supercritical pressure low boiling point medium M5 is heated by heat exchange with the heat source medium F1. Here, the low boiling point medium M5 having a supercritical pressure is heated by heat exchange so as to rise from a temperature lower than the critical temperature TC to a temperature exceeding the critical temperature TC and the pseudocritical temperature TE (see FIG. 11). The Then, the supercritical pressure low boiling point medium M2 subjected to the heat exchange flows from the supercritical pressure fluid heat exchanger 2 into the medium turbine 3 as a working medium.

  The detailed configuration of the supercritical fluid heat exchanger 2 will be described later.

[A-2] Medium turbine 3
The medium turbine 3 is driven by a supercritical low-boiling point medium M2 heated by heat exchange in the supercritical fluid heat exchanger 2 as a working medium.

  Specifically, in the medium turbine 3, a pipe in which the main steam stop valve VM2 (MSV) is installed is provided between the supercritical pressure fluid heat exchanger 2 and the supercritical fluid is exchanged via the pipe. A low boiling point medium M2 having a pressure flows as a working medium. And the turbine rotor (illustration omitted) installed in the inside of a casing (illustration omitted) rotates the medium turbine 3 by supply of the low boiling-point medium M2 of the supercritical pressure.

  The medium turbine 3 is, for example, a multi-stage axial flow turbine, and a turbine stage composed of stationary blades (nozzle blades) and moving blades (turbine blades) is arranged in a plurality of stages along the rotation axis of the turbine rotor. , Provided. The supercritical low-boiling medium M2 is supplied to the first stage turbine stage located at one end of the medium turbine 3 and then sequentially performs work in each turbine stage to rotate the turbine rotor. Supercritical low-boiling point medium M2 is exhausted after passing through the last stage turbine stage located at the other end, the pressure and temperature decrease as it flows from one end to the other end. .

  In the medium turbine 3, a generator 3G is connected to the rotating shaft of the turbine rotor, and the generator 3G is driven by the rotation of the turbine rotor to generate electric power.

  In the present embodiment, as described above, the case where the medium turbine 3 is an axial flow type is described, but the present invention is not limited thereto. The medium turbine 3 may be of various types such as a radial flow type (width flow type).

[A-3] Condenser 4
The condenser 4 cools and condenses the low boiling point medium M3 exhausted from the medium turbine 3. The condenser 4 condenses the low boiling point medium M3 using the cooling water f62 supplied from the cooling water supply unit 6.

  Specifically, the condenser 4 is provided with a pipe between the outlet of the medium turbine 3 and the low boiling point medium M3 flows from the medium turbine 3 through the pipe. At the same time, the condenser 4 is provided with a pipe between the cooling water supply unit 6 and the cooling water f62 flows from the cooling water supply unit 6 through the pipe. And in the condenser 4, heat exchange is performed between the low boiling point medium M3 and the cooling water f62.

  In the condenser 4, the low boiling point medium M3 is cooled by heat exchange with the cooling water f62 and condensed and liquefied. Then, the liquid low boiling point medium M4 flows out of the condenser 4.

  On the other hand, in the condenser 4, the cooling water f62 is heated by heat exchange with the low boiling point medium M3. And the cooling water f4 after the heat exchange flows out of the condenser 4 to the outside.

[A-4] Supercritical pressure medium pump 5
The supercritical pressure medium pump 5 raises the low boiling point medium M4 condensed in the condenser 4 to a supercritical pressure and sends it to the supercritical pressure fluid heat exchanger 2.

  Specifically, a pipe is provided between the supercritical pressure medium pump 5 and the condenser 4, and a liquid low boiling point medium M 4 flows from the condenser 4 through the pipe. Then, the supercritical pressure medium pump 5 pressurizes the low boiling point medium M4 to the supercritical pressure, and the boosted supercritical pressure low boiling point medium M5 is transferred to the supercritical pressure fluid heat exchanger 2.

[A-5] Cooling water supply unit 6
The cooling water supply unit 6 includes a cooling water pump 61, a cooler 62, and a cooling fan 63, and supplies the cooling water f 62 to the condenser 4.

  Specifically, in the cooling water supply unit 6, the cooling water pump 61 sucks the cooling water f1 from the outside, and sends the sucked cooling water f61 to the cooler 62. In the cooler 62, the cooling water f61 is cooled by cooling air from the cooling fan 63. Then, the cooling water f62 cooled by the cooler 62 is supplied to the condenser 4.

[B] Detailed Configuration of Supercritical Pressure Fluid Heat Exchanger 2 FIG. 2, FIG. 3 and FIG. 4 are diagrams showing the main part of the supercritical pressure fluid heat exchanger 2 in the power generation system according to the first embodiment. .

  FIG. 2 shows a cross section, in which the flow of the heat source media F1 and F2 is indicated by solid arrows, and the flow of the low boiling point media M2 and M5 at supercritical pressure is indicated by dashed arrows. 3A shows a cross section of the Xa-Xa portion in FIG. 2, and FIG. 3B shows a cross section of the Xg-Xg portion in FIG. FIG. 4 shows a cross section of the portion X1-X1 in FIG.

  As shown in FIGS. 2, 3, and 4, the supercritical fluid heat exchanger 2 is a multi-tube (shell and tube type) heat exchanger, and includes a heat transfer tube 21, a body 22, and a tube plate 23. A water chamber portion 24 and a baffle plate 25.

  The supercritical pressure fluid heat exchanger 2 includes a portion in which the heat source medium F1 and the supercritical pressure low boiling point medium M5 flow toward each other and a portion in which the heat source medium F1 and the low boiling point medium M5 flow at right angles to each other. This is done to heat the supercritical low boiling point medium M5.

  The detail of each part which comprises the supercritical pressure fluid heat exchanger 2 is demonstrated sequentially.

[B-1] Heat transfer tube 21 (tube)
As shown in FIGS. 2, 3, and 4, a plurality of heat transfer tubes 21 are arranged inside the body 22 with a space therebetween. Each of the plurality of heat transfer tubes 21 is a cylindrical smooth tube, and is installed such that the central axis (tube axis) is along the horizontal direction.

  As shown in FIG. 2, in each of the plurality of heat transfer tubes 21, the heat source medium F1 flows from the inlet 21A located at the left end (one end) and flows inside. Then, the heat source medium F2 flows out from the outlet 21B located at the right end (the other end).

[B-2] Body 22 (shell)
As shown in FIGS. 2 and 3, the body 22 is a cylindrical tube, and is installed so that the central axis 22 </ b> C is along the horizontal direction, like each of the plurality of heat transfer tubes 21.

  As shown in FIG. 2, an introduction pipe 22 </ b> A is installed on the right end (one end) side of the outer peripheral surface of the body 22. The introduction pipe 22 </ b> A has a central axis along the vertical direction, and an upper end (one end) is connected to the body 22.

  In addition, a discharge pipe 22 </ b> B is installed on the left end (other end) side of the outer peripheral surface of the body 22. The discharge pipe 22 </ b> B has a central axis in the vertical direction and a lower end (one end) connected to the body 22.

  In the cylinder 22, the supercritical pressure low boiling point medium M5 flows from the outside into the inside through the introduction rod 22A, and the supercritical pressure low boiling point medium M2 flows out from the inside to the outside through the discharge pipe 22B. To do.

[B-3] Tube plate 23 (tube plate)
2 and 4, the tube plate 23 is, for example, a disk-like plate body having a diameter larger than the outer diameter of the body 22, and the right end (one end) and the left end (the other end) of the body 22. ) And a pair of the two faces each other.

  In each of the pair of tube plates 23, both end portions (right end portion, left end portion) of the heat transfer tube 21 pass therethrough and support each of the plurality of heat transfer tubes 21.

  Specifically, among the pair of tube plates 23, the tube plate 23 installed at the right end of the trunk 22 has a portion on the right end side through the plurality of heat transfer tubes 21. In addition, among the pair of tube plates 23, the tube plate 23 installed at the left end of the body 22 has a portion on the left end side of the plurality of heat transfer tubes 21 passing therethrough.

[B-4] Water chamber 24 (bonnet, header)
As shown in FIG. 2, the water chamber portion 24 has, for example, a hemispherical shape, and is provided so that a pair faces each other at the right end and the left end of the trunk 22.

  Out of the pair of water chamber portions 24, the water chamber portion 24 installed at the right end of the trunk 22 is provided with a discharge pipe 24B. The discharge pipe 24 </ b> B has a central axis in the horizontal direction and is connected to the water chamber portion 24 at the left end. In the discharge pipe 24 </ b> B, the heat source medium F <b> 2 flows from the left end to the right end, and the heat source medium F <b> 2 flows out of the water chamber portion 24 from the right end.

  In addition, an introduction pipe 24 </ b> A is installed in the water chamber 24 installed at the left end of the trunk 22 among the pair of water chambers 24. The introduction pipe 24 </ b> A has a central axis along the horizontal direction and is connected to the water chamber portion 24 at the right end. In the introduction pipe 24A, the heat source medium F1 flows from the left end to the right end, and the heat source medium F1 flows into the water chamber portion 24 from the right end.

[B-5] Baffle plate 25 (baffle plate)
As shown in FIG. 2, a plurality of baffle plates 25 are arranged in the body 22 at intervals in the horizontal direction. For example, first to eighth baffle plates 25a to 25h are sequentially installed as baffle plates 25 from the introduction pipe 22A (inlet) side to the discharge pipe 22B (outlet) side in the body 22. Yes.

  As shown in FIG. 2, the first to eighth baffle plates 25 a to 25 h have the same thickness and are installed so as to stand in the vertical direction with respect to the heat transfer tube 21 inside the body 22. Yes. The first to eighth baffle plates 25a to 25h sequentially pass through the space inside the body 22 from the introduction pipe 22A (inlet) side to the discharge pipe 22B (outlet) side in order from the first to the ninth. It is divided into chambers R1 to R9.

  As shown in FIGS. 2 and 3A, the first baffle plate 25 a is a plate-like body, and a notch 25 </ b> K is formed in a circular plate having a diameter smaller than the inner diameter of the body 22. . As shown in FIG. 3A, the first baffle plate 25a has a cut-out shape in plan view, and the cut-out portion 25K is divided by a cut-out line 25L along the horizontal direction. It corresponds to one part.

  As shown in FIGS. 2 and 3 (b), the seventh baffle plate 25g is a notch-shaped plate-like body in which a cutout portion 25K is formed, like the first baffle plate 25a.

  The other baffle plates (second to sixth baffle plates 25b to 25f, eighth baffle plate 25h) other than the first baffle plate 25a and the seventh baffle plate 25g are not shown in the plan view. However, as in the above, each is a plate-like body having a notch shape in which a notch 25K is formed.

  As shown in FIG. 2, each of the first to eighth baffle plates 25 a to 25 h includes a supercritical low-boiling medium M5 from the introduction pipe 22 </ b> A (inlet) to the discharge pipe 22 </ b> B (outlet). It is installed to meander and flow toward. Here, each of the first to eighth baffle plates 25a to 25h has an inner peripheral surface of the barrel 22 so that the positions of the cutout portions 25K are alternately arranged via the central axis 22C of the barrel 22 in the horizontal direction. It is fixed to.

  Specifically, among the plurality of baffle plates 25, the first baffle plate 25 a has the cutout portion 25 </ b> K positioned above the central axis 22 </ b> C of the body 22. In the body 22, the second baffle plate 25 b installed next to the first baffle plate 25 a is opposite to the first baffle plate 25 a, and the notch portion 25 </ b> K has a central axis 22 </ b> C of the body 22. Is located below.

  Similarly to the first baffle plate 25a, each of the third baffle plate 25c, the fifth baffle plate 25e, and the seventh baffle plate 25g has a notch 25K above the central axis 22C of the body 22. positioned. On the other hand, each of the fourth baffle plate 25d, the sixth baffle plate 25f, and the eighth baffle plate 25h has a notch portion 25K with the central axis of the barrel 22 as with the second baffle plate 25b. It is located below 22C. As a result, the supercritical low-boiling point medium M5 sequentially passes through each of the cutout portions 25K of the first to eighth baffle plates 25a to 25h in the body 22 to introduce the introduction pipe 22A (inlet). ) To meander to the discharge pipe 22B (exit).

  FIG. 5 is a cross-sectional view showing in detail the arrangement of the plurality of baffle plates 25 in the supercritical fluid heat exchanger 2 of the power generation system according to the first embodiment. FIG. 5 shows the same cross section as FIG. 2, but the description of the heat transfer tube 21 is omitted.

  As shown in FIG. 5, each of the first to eighth baffle plates 25 a to 25 h is between one baffle plate 25 and another baffle plate 25 installed next to the one baffle plate 25. The distance D (= Dab, Dbc,... Dgh) is set so as to become longer sequentially along the flow of the low boiling point medium M5 having a supercritical pressure inside the cylinder 22.

  Specifically, the distance Dbc between the second baffle plate 25b and the third baffle plate 25c is longer than the distance Dab between the first baffle plate 25a and the second baffle plate 25b. . The distance Dcd between the third baffle plate 25c and the fourth baffle plate 25d is longer than the distance Dbc between the second baffle plate 25b and the third baffle plate 25c. Thus, the distance Dab between the first baffle plate 25a and the second baffle plate 25b, the distance Dbc between the second baffle plate 25b and the third baffle plate 25c, and the third baffle plate 25c. Dcd between the fourth baffle plate 25d, the distance Dde between the fourth baffle plate 25d and the fifth baffle plate 25e, and between the fifth baffle plate 25e and the sixth baffle plate 25f And the distance Dfg between the sixth baffle plate 25f and the seventh baffle plate 25g and the distance Dgh between the seventh baffle plate 25g and the eighth baffle plate 25h become longer. (That is, Dab <Dbc <Dcd <Dde <Def <Dfg <Dgh).

  That is, the gap between the pair of baffle plates 25 adjacent inside the cylinder 22 is gradually increased along the flow of the low boiling point medium M5 having a supercritical pressure inside the cylinder 22, and accordingly, The volumes of the second to eighth chambers R2 to R8 partitioned by the plurality of baffle plates 25 are sequentially increased.

  In addition, in the present embodiment, each of the first to eighth baffle plates 25a to 25h has an area S (= Sa, Sb,...) Of the notch 25K, as can be seen from FIGS. , Sh) is formed so as to increase along the flow of the low boiling point medium M5 having a supercritical pressure inside the cylinder 22.

  Specifically, as shown in FIG. 5, each of the first to eighth baffle plates 25 a to 25 h is the maximum distance between the notch line 25 </ b> L of the notch 25 </ b> K and the inner peripheral surface of the trunk 22. Ya to Yh sequentially increase along the flow of the low-boiling medium M5 having a supercritical pressure inside the cylinder 22 (Ya <Yb <Yc <Yd <Ye <Yf <Yg <Yh). Therefore, as can be seen from FIGS. 3 and 5, in each of the first to eighth baffle plates 25a to 25h, the areas Sa to Sh of the cut portions 25K through which the low-boiling point medium M5 having a supercritical pressure passes are sequentially increased. Is getting wider. That is, the area Sa of the cutout portion 25K of the first baffle plate 25a, the area Sb of the cutout portion 25K of the second baffle plate 25b, the area Sc of the cutout portion 25K of the third baffle plate 25c, the fourth The area Sd of the cutout portion 25K of the baffle plate 25d, the area Se of the cutout portion 25K of the fifth baffle plate 25e, the area Sf of the cutout portion 25K of the sixth baffle plate 25f, and the cutout of the seventh baffle plate 25g The area Sg of the cutout portion 25K and the area Sh of the cutout portion 25K of the eighth baffle plate 25h increase in the order (Sa <Sb <Sc <Sd <Se <Sf <Sg <Sh).

  Further, in each of the first to eighth baffle plates 25a to 25h, as shown in FIGS. 2 and 3, a plurality of through holes are formed, and a heat transfer tube 21 is provided in each of the plurality of through holes. It penetrates horizontally.

  In each of the plurality of baffle plates 25, between one baffle plate (for example, 25a) and another baffle plate (for example, 25b) installed next to the one baffle plate (for example, 25a). The distance D (= Dab, Dbc,..., Dgh) is preferably different according to the change in the density of the low-boiling medium M5 having a supercritical pressure inside the cylinder 22. In this case, the distance D between each of the plurality of baffle plates 25 is sequentially increased in proportion to the reciprocal of the ratio (density ratio) at which the density of the low boiling point medium M5 with supercritical pressure changes inside the cylinder 22. It is preferable to become.

  For example, the density ρgh when the low boiling point medium M5 of supercritical pressure passes between the seventh baffle plate 25g and the eighth baffle plate 25h is the first baffle plate 25a and the second baffle plate 25b. It is assumed that the density ρab when passing through the middle is 1/2 times (that is, ρgh / ρab = 1/2). In this case, the distance Dgh between the seventh baffle plate 25g and the eighth baffle plate 25h is twice the distance Dab between the first baffle plate 25a and the second baffle plate 25b. (That is, Dgh / Dab = 2 (= ρab / ρgh)).

  In addition, in each of the plurality of baffle plates 25, the cutout portion 25 </ b> K has different areas Sa to Sh according to the change in the density of the supercritical low-boiling medium M <b> 5 inside the body 22. Is preferred. In this case, the areas Sa to Sh of the notch portions 25K of the plurality of baffle plates 25 are proportional to the reciprocal of the ratio (density ratio) at which the density of the low-boiling medium M5 with supercritical pressure changes inside the cylinder 22. Thus, it is preferable that the width gradually increases.

  For example, the density ρh when the low boiling point medium M5 of supercritical pressure passes through the notch 25K of the eighth baffle plate 25h is less than the density ρa when passing through the first baffle plate 25a. Suppose that it has doubled (that is, ρh / ρa = 1/2). In this case, it is preferable to double the area Sh of the cutout portion 25K of the eighth baffle plate 25h with respect to the area Sa of the cutout portion 25K of the first baffle plate 25a (that is, Sh / Sa = 2 (= ρa / ρh)).

[C] Operation The operation of the supercritical fluid heat exchanger 2 will be described with reference to FIGS.

  Here, the operation of the supercritical fluid heat exchanger 2 will be described in detail separately for each of the flow of the heat source media F1 and F2 and the flow of the low boiling point media M2, M3, M4, and M5.

[C-1] Heat source mediums F1 and F2 In the supercritical fluid heat exchanger 2, as shown in FIG. 1, the heat source medium F1 flows from the heat source medium supply source 1. The heat source medium F1 is subjected to heat exchange with the supercritical pressure low boiling point medium M5 in the supercritical pressure fluid heat exchanger 2. Thereafter, the heat source medium F2 subjected to the heat exchange flows out from the supercritical fluid heat exchanger 2 to the outside.

  Specifically, as shown in FIG. 2, the heat source medium F1 first flows into the interior (water chamber) of the water chamber portion 24 installed at the left end of the trunk 22 via the introduction pipe 24A.

  Next, in each of the plurality of heat transfer tubes 21, the heat source medium F1 flows from the inlet 21A located at the left end and flows inside. At this time, the heat source medium F1 exchanges heat with the supercritical low-boiling point medium M5 flowing around the plurality of heat transfer tubes 21.

  Next, in each of the plurality of heat transfer tubes 21, the heat source medium F <b> 1 flows out from the outlet 21 </ b> B located at the right end and flows into the water chamber 24 (water chamber) installed at the right end of the trunk 22.

  Next, the heat source medium F2 flows out from the inside of the water chamber part 24 installed at the right end of the trunk 22 to the outside through the discharge pipe 24B.

[C-2] Low-boiling point media M2, M3, M4, and M5 As shown in FIG. 1, the low-boiling point media M2, M3, M4, and M5 include a supercritical fluid heat exchanger 2, a medium turbine 3, and a condenser. 4 and the supercritical pressure medium pump 5 are sequentially circulated.

  Here, as shown in FIG. 1, the low boiling point medium M2 flows from the supercritical fluid heat exchanger 2 into the medium turbine 3 as a working medium, drives the generator 3G, and then discharges from the medium turbine 3. Is done. Next, the low boiling point medium M <b> 3 flows from the medium turbine 3 into the condenser 4 and is condensed by the condenser 4. Next, the low boiling point medium M4 condensed by the condenser 4 flows into the supercritical pressure medium pump 5, and is boosted to the supercritical pressure by the supercritical pressure medium pump 5 and transferred. Next, the supercritical pressure low boiling point medium M <b> 5 boosted by the supercritical pressure medium pump 5 flows into the supercritical pressure fluid heat exchanger 2. That is, the low boiling point media M2, M3, M4, and M5 circulate through the respective parts by the Rankine cycle.

  As shown in FIG. 2, in the supercritical fluid heat exchanger 2, a supercritical pressure low boiling point medium M5 flows into the interior of the cylinder 22 and flows through the interior, and is heated by heat exchange with the heat source medium F1. Is done.

  Specifically, the low boiling point medium M5 having a supercritical pressure is placed in the first chamber R1 located between the tube plate 23 installed at the right end and the first baffle plate 25a in the body 22. Then, it flows in through the introduction pipe 22A. Then, the supercritical low boiling point medium M5 flows from the lower part to the upper part in the first chamber R1.

  Next, the low boiling point medium M5 having a supercritical pressure is positioned between the first baffle plate 25a and the second baffle plate 25b via the notch 25K positioned above the first baffle plate 25a. It flows into the second chamber R2. Then, the supercritical low boiling point medium M5 flows from the upper part to the lower part in the second chamber R2.

  Next, the supercritical low boiling point medium M5 is positioned between the second baffle plate 25b and the third baffle plate 25c via a notch 25K formed below the second baffle plate 25b. Into the third chamber R3. Then, the supercritical low boiling point medium M5 flows from the lower part to the upper part in the third chamber R3.

  As described above, the low-boiling point medium M5 having a supercritical pressure meanders inside the cylinder 22 and sequentially flows through each of the first to ninth chambers R1 to S9.

  Finally, the low boiling point medium M2 having a supercritical pressure flows out from the inside of the cylinder 22 through the discharge pipe 22B.

  As described above, when the low boiling point medium M5 having a supercritical pressure flows through the body 22, heat exchange with the heat source medium F1 is performed in each of the first to ninth chambers R1 to S9, and sequentially, The temperature rises. Here, the supercritical pressure low boiling point medium M5 rises from a temperature lower than the critical temperature TC to a temperature exceeding the critical temperature TC and the pseudocritical temperature TE in the supercritical pressure fluid heat exchanger 2. At this time, the supercritical low-boiling point medium M5 has a lower density ρ as the temperature T increases, and when the temperature exceeds the vicinity of the critical temperature TC, the density ρ decreases rapidly (see FIG. 11).

  However, in the present embodiment, the distance D between the plurality of baffle plates 25 is sequentially increased along the flow of the supercritical low-boiling medium M5 inside the cylinder 22. At the same time, each of the plurality of baffle plates 25 has an area S of the cutout portion 25 </ b> K that sequentially increases along the flow of the supercritical low-boiling-point medium M <b> 5 inside the body 22.

  For this reason, in this embodiment, even if the density ρ of the low-boiling-point medium M5 having a supercritical pressure rapidly decreases due to the increase in the temperature T, the pressure changes in each of the first to ninth chambers R1 to S9. Can be suppressed. As a result, in this embodiment, since the flow velocity of the low boiling point medium M5 having a supercritical pressure does not increase rapidly, it is possible to prevent an increase in pressure loss. The pressure loss mainly occurs at the center of the tube group, but in this embodiment, the pressure loss at the center of the tube group can be brought close to the pressure loss in the supercritical pressure liquid state. It is.

[D] Summary As described above, in the power generation system of the present embodiment, the supercritical fluid heat exchanger 2 performs heat exchange between the supercritical low-boiling medium M5 and the heat source medium F1, and the supercritical pressure is obtained. The low boiling point medium M5 having a pressure is heated to a temperature exceeding the critical temperature TC and the pseudocritical temperature TE.

  The supercritical fluid heat exchanger 2 includes a heat transfer tube 21, a body 22, and a baffle plate 25. The heat transfer tube 21 is accommodated inside the trunk 22, and the heat source medium F1 flows through the inside. In the body 22, the low boiling point medium M <b> 5 having a supercritical pressure flows around the heat transfer tube 21 inside. A plurality of baffle plates 25 are installed inside the cylinder 22 so as to be spaced apart from each other so that the low boiling point medium M5 having a supercritical pressure flows meandering from the inlet toward the outlet. .

  Here, as described above, the plurality of baffle plates 25 are distances D (= Dab, Dbc) between one baffle plate 25 and another baffle plate 25 installed next to the one baffle plate 25. ,..., Dgh) are installed so as to be long along the flow of the low boiling point medium M5 having a supercritical pressure inside the cylinder 22.

  Therefore, in the present embodiment, as described above, even if the supercritical pressure low boiling point medium M5 exceeds the vicinity of the critical temperature TC and the density ρ rapidly decreases, the flow rate of the supercritical pressure low boiling point medium M5 is Since it does not rise rapidly, it is possible to prevent the pressure loss from increasing.

  As a result, in this embodiment, efficiency can be easily realized in the power generation system.

  In addition, in this embodiment, in each of the plurality of baffle plates 25, the notch 25 </ b> K has an area S (= Sa, Sa) along the flow of the supercritical low-boiling medium M <b> 5 inside the cylinder 22. Sb,..., Sh) are formed to be large.

  For this reason, in this embodiment, it can prevent more effectively that a pressure loss increases.

[E] Modifications As described above, in the present embodiment, eight of the first to eighth baffle plates 25a to 25h are installed as the baffle plate 25, but the present invention is not limited to this. Of course, more than eight baffle plates 25 may be installed, or less than eight baffle plates 25 may be installed.

  As described above, in the present embodiment, the distance D (= Dab, Dbc,..., Dgh) between the plurality of baffle plates 25 is the flow of the low-boiling point medium M5 having a supercritical pressure inside the cylinder 22. A plurality of baffle plates 25 are installed so as to be longer along the line. At the same time, in the present embodiment, in each of the plurality of baffle plates 25, the notch 25 </ b> K has an area S (= Sa, Sb) along the flow of the supercritical low-boiling medium M <b> 5 inside the cylinder 22. ,..., Sh) are formed to be large. However, it is not limited to this. The cutout portions 25K of the plurality of baffle plates 25 may be formed such that the area S is sequentially increased along the flow of the supercritical low-boiling medium M5 inside the barrel 22 as necessary. Good.

  As described above, in the present embodiment, each of the distances D (= Dab, Dbc,..., Dgh) between the plurality of baffle plates 25 is a low-boiling medium M5 having a supercritical pressure inside the cylinder 22. (That is, Dab <Dbc <Dcd <Dde <Def <Dfg <Dgh). However, the present invention is not limited to this. The plurality of baffle plates 25 so that the distance D (= Dab, Dbc,..., Dgh) between the plurality of baffle plates 25 is longer on the outlet side than the inlet side of the supercritical low-boiling medium M5. May be installed. For example, in the portion on the inlet side, the distance D between the plurality of baffle plates 25 is equal, and in the portion on the outlet side, the distance D between the plurality of baffle plates 25 corresponds to the flow of the low boiling point medium M5 having a supercritical pressure. You may comprise so that it may become long along (for example, Dab = Dbc = Dcd = Dde <Def <Dfg <Dgh). Similarly, the area S (= Sa, Sb,..., Sh) of the notch 25K is also configured to be larger on the outlet side than on the inlet side of the low boiling point medium M5 having a supercritical pressure. Also good. For example, the area S at the inlet side may be equal, and the area S may be increased along the flow of the low boiling point medium M5 having a supercritical pressure at the outlet side (for example, Sa = Sb). = Sc = Sd <Se <Sf <Sg <Sh).

  As described above, in this embodiment, the power generation system includes the supercritical fluid heat exchanger 2, the medium turbine 3, the condenser 4, the supercritical pressure medium pump 5, and the cooling water supply unit 6. However, devices other than these may be provided separately. For example, devices such as a regenerator, a gas-liquid separator, and a bypass valve may be installed as appropriate.

Second Embodiment
[A] Configuration, etc. FIGS. 6, 7, and 8 are diagrams illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the second embodiment.

  FIG. 6 shows a cross section similar to FIG. In FIG. 6, unlike the case of FIG. 2, a part of the flow of the heat source medium F1 and the flow of the low boiling point medium M5 having a supercritical pressure is omitted, but as in the case of FIG. F1 and supercritical low boiling point medium M5 flow. 7 shows a cross section of the Xfg-Xfg portion in FIG. 6, and FIG. 8 shows a cross section of the Xgh-Xgh portion in FIG.

  As shown in FIGS. 6, 7, and 8, in the power generation system according to the present embodiment, the supercritical fluid heat exchanger 2 further includes a heat transfer tube support portion 26 (vibration suppression portion). This embodiment is the same as the case of the first embodiment except for the above points and related points. For this reason, in this embodiment, about the part which overlaps with said embodiment, description is abbreviate | omitted suitably.

  As shown in FIGS. 6, 7, and 8, the heat transfer tube support portion 26 is installed inside the body 22, supports the heat transfer tube 21, and suppresses generation of vibration.

  Here, the heat transfer tube support portion 26 is installed in a portion located on the outlet side (discharge tube 22B) of the supercritical low-boiling-point medium M5 inside the barrel 22. That is, the heat transfer tube support portion 26 is not installed on the narrow inlet side (the side of the introduction tube 22 </ b> A) between the plurality of baffle plates 25 in the body 22, and between the plurality of baffle plates 25. It is installed on the wide outlet side (the side of the discharge pipe 22B).

  In this embodiment, as shown in FIGS. 6, 7, and 8, a support grid 261, a first support plate 262 </ b> A, and a second support plate 262 </ b> B are installed as the heat transfer tube support portion 26. .

  Each part which comprises the heat exchanger tube support part 26 is demonstrated sequentially.

[A-1] Support grid 261
As shown in FIG. 6, the support lattice 261 is disposed in the middle of the body 22 between the sixth baffle plate 25 f and the seventh baffle plate 25 g. That is, the support lattice 261 is provided in the seventh chamber R7.

  As shown in FIG. 7, the support grid 261 is configured by arranging a plurality of rod-shaped bodies along the arrangement of the plurality of heat transfer tubes 21 between the plurality of heat transfer tubes 21.

  The support grid 261 has a plurality of heat transfer tubes 21 penetrating through the openings defined by the plurality of rod-shaped bodies, and supports the plurality of heat transfer tubes 21 penetrating through the openings.

  In the seventh chamber R7 in which the support grid 261 is provided, the supercritical low-boiling-point medium M5 flows through the opening of the support grid 261 from below to above.

[A-2] First support plate 262A
As shown in FIG. 6, the first support plate 262A is installed in the middle of the seventh baffle plate 25g and the eighth baffle plate 25h in the body 22. That is, the first support plate 262A is provided in the eighth chamber R8. Here, the surface of the first support plate 262A is along the vertical direction, similarly to the seventh baffle plate 25g and the eighth baffle plate 25h.

  As shown in FIGS. 6 and 8, the first support plate 262A is a plate-like body, and the same notch portion 262K as the notch portion 25K formed in the seventh baffle plate 25g is formed at the same position. Has been. At the same time, the first support plate 262A has the same notch portion 262K formed at the same position as the notch portion 25K formed in the eighth baffle plate 25h.

  In the first support plate 262A, the plurality of heat transfer tubes 21 pass through the through holes, and support the plurality of heat transfer tubes 21 that have passed through the through holes.

  In the eighth chamber R8 in which the first support plate 262A is provided, the supercritical low-boiling point medium M5 flows along the both surfaces of the first support plate 262A from the upper side to the lower side.

[A-3] Second support plate 262B
As shown in FIG. 6, the second support plate 262 </ b> B is installed inside the cylinder 22 between the eighth baffle plate 25 h and the tube plate 23 installed at the left end of the cylinder 22. That is, the second support plate 262B is provided in the ninth chamber R9. Here, the surface of the second support plate 262B is along the vertical direction, similar to the eighth baffle plate 25h and the tube plate 23 installed at the left end of the barrel 22.

  Although the illustration of the planar shape is omitted, the second support plate 262B has a notch 262K as in the case of the first support plate 262A (see FIG. 8).

  Similarly to the first support plate 262A, the second support plate 262B has a plurality of heat transfer tubes 21 passing through the through holes, and supports the plurality of heat transfer tubes 21 penetrating the through holes.

  In the ninth chamber R9 in which the second support plate 262B is provided, the supercritical low-boiling-point medium M5 flows along both surfaces of the second support plate 262B from below to above.

[B] Summary As described above, in the supercritical fluid heat exchanger 2 of the present embodiment, a portion located on the outlet (exhaust pipe 22B) side of the supercritical low-boiling-point medium M5 in the cylinder 22 is provided. The heat transfer tube support part 26 is installed. The heat transfer tube support portion 26 is provided between a pair of adjacent baffle plates 25 or between the adjacent baffle plates 25 and the tube plate 23. Here, as the heat transfer tube support portion 26, a support grid 261, a first support plate 262A, and a second support plate 262B are installed to support the heat transfer tube 21.

  As in the case of the first embodiment, among the inside of the cylinder 22, the outlet side of the supercritical pressure low boiling point medium M <b> 5 (the side of the discharge pipe 22 </ b> B) is sandwiched between a pair of baffle plates 25 adjacent in the heat transfer pipe 21. The portion to be removed is longer than the inlet side (the introduction pipe 22A side). In that portion, the low boiling point medium M5 having a supercritical pressure flows in a direction orthogonal to the central axis of the heat transfer tube 21. For this reason, the heat transfer tube 21 may vibrate greatly.

  However, in the present embodiment, as described above, the heat transfer tube support portion 26 is installed in the portion where the heat transfer tube 21 vibrates and supports the heat transfer tube 21.

  Therefore, in this embodiment, vibration of the heat transfer tube 21 can be suppressed.

[C] Modified Example As described above, in the present embodiment, three of the support grid 261, the first support plate 262A, and the second support plate 262B are installed as the heat transfer tube support portion 26. Not limited to this. For example, the support grid 261, the first support plate 262A, and the second support plate 262B may be installed.

<Third Embodiment>
[A] Configuration, etc. FIG. 9 is a diagram illustrating a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the third embodiment.

  FIG. 9 shows a cross section similar to FIG. In FIG. 9, unlike the case of FIG. 2, a part of the flow of the heat source medium F1 and the flow of the low boiling point medium M5 having a supercritical pressure is omitted, but as in the case of FIG. F1 and supercritical low boiling point medium M5 flow.

  As shown in FIG. 9, in the power generation system of the present embodiment, the supercritical fluid heat exchanger 2 has an uneven portion 21 </ b> F formed on a part of the outer peripheral surface of the heat transfer tube 21. This embodiment is the same as the case of the first embodiment except for the above points and related points. For this reason, in this embodiment, about the part which overlaps with said embodiment, description is abbreviate | omitted suitably.

  As shown in FIG. 9, the uneven portion 21 </ b> F is formed in a portion of the outer peripheral surface of the plurality of heat transfer tubes 21 that is located on the outlet (exhaust tube 22 </ b> B) side of the supercritical pressure low boiling point medium M <b> 5.

  Here, the concavo-convex portion 21 </ b> F is a supercritical pressure low boiling point medium M <b> 5 of the first to ninth chambers R <b> 1 to R <b> 9 defined by the plurality of baffle plates 25 and the pair of tube plates 23 inside the body 22. It is formed in sixth to ninth chambers R6 to R9 located on the outlet (exhaust pipe 22B) side. The uneven portion 21F is not formed in the first to fifth chambers R1 to R5 located on the inlet (introduction tube 22A) side of the supercritical low boiling point medium M5, and in this portion, the heat transfer tube 21 The outer peripheral surface is smooth.

  Specifically, in the sixth chamber R6, the uneven portion 21F is formed on the outer peripheral surface of the heat transfer tube 21 located in the lower portion. In each of the seventh chamber R7 to the ninth chamber R9, the uneven portion 21F is formed over the entire outer peripheral surface of the heat transfer tube 21.

  In the uneven portion 21 </ b> F, for example, a plurality of fins are formed so as to protrude outward from the outer peripheral surface of the heat transfer tube 21. The plurality of fins are so-called low fins, and are formed, for example, by rolling the outer peripheral surface of the heat transfer tube 21.

[B] Summary As described above, in the supercritical fluid heat exchanger 2 of the present embodiment, of the outer peripheral surfaces of the plurality of heat transfer tubes 21, the outlet side (exhaust tube 22B) of the supercritical pressure low boiling point medium M5. A concave-convex portion 21F is formed in a portion located at. For example, a plurality of fins are formed in the uneven portion 21F.

  In the present embodiment, as in the case of the first embodiment, the interval between the pair of adjacent baffle plates 25 in the body 22 is set on the outlet (exhaust pipe 22B) side of the supercritical low-boiling medium M5. Since this is wider than the inlet (introduction pipe 22A) side, the flow rate of the low boiling point medium M5 having a supercritical pressure becomes slow, and the heat transfer rate may be lowered.

  However, in the present embodiment, as described above, on the outlet side of the low boiling point medium M5 with supercritical pressure, the uneven portion 21F is formed on the outer peripheral surface of the heat transfer tube 21, and the low boiling point medium M5 with supercritical pressure is formed. The contact area in contact with the heat transfer tube 21 is increased.

  Therefore, in this embodiment, heat transfer performance can be improved.

[C] Modified Example As described above, in the present embodiment, the case where the uneven portion 21 </ b> F is provided by forming fins on the outer peripheral surface of the heat transfer tube 21 is not limited thereto. As long as the area where the heat transfer tube 21 and the low-boiling point medium M5 with supercritical pressure are in contact with each other increases, it may be other than fins.

<Fourth embodiment>
[A] Configuration, etc. FIG. 10 is a diagram showing a main part of the supercritical fluid heat exchanger 2 in the power generation system according to the fourth embodiment.

  FIG. 10 shows a cross section similar to FIG. In FIG. 10, as in FIG. 9, a part of the flow of the heat source medium F <b> 1 and the flow of the low boiling point medium M <b> 5 having a supercritical pressure is omitted, and as in the case of FIG. 2, the heat source medium F <b> 1 and A low boiling point medium M5 of supercritical pressure flows.

  As shown in FIG. 10, in the power generation system of the present embodiment, the supercritical fluid heat exchanger 2 has a range in which the uneven portion 21 </ b> F is formed on the outer peripheral surface of the heat transfer tube 21 in the case of the third embodiment. (See FIG. 9). The present embodiment is the same as the third embodiment except for the above points and related points. For this reason, in this embodiment, about the part which overlaps with said embodiment, description is abbreviate | omitted suitably.

  As shown in FIG. 10, the concavo-convex portion 21F is formed at the outlet (discharge) of the low boiling point medium M5 having a supercritical pressure among the outer peripheral surfaces of the plurality of heat transfer tubes 21, as in the case of the third embodiment (see FIG. 9). It is formed in a portion located on the tube 22B) side. Here, the concavo-convex portion 21 </ b> F is an outlet (exhaust pipe) of the supercritical low-boiling-point medium M <b> 5 among the plurality of chambers R <b> 1 to R <b> 9 partitioned by the plurality of baffle plates 25 and the pair of tube plates 23 inside the body 22. 22B) are formed in the respective chambers R7 to R9. The uneven portion 21F is not formed in the chambers R1 to R6 located on the inlet (introduction tube 22A) side of the supercritical pressure low boiling point medium M5.

  However, unlike the case of the third embodiment, uneven portions 21F are not formed on the outer peripheral surface of the portion of the plurality of baffle plates 25 penetrating through the notch portions 25K between each of the plurality of baffle plates 25. The outer peripheral surface is smooth. That is, in each of the seventh chamber R7, the eighth chamber R8, and the ninth chamber R9, the outer peripheral surface of the heat transfer tube 21 with respect to the portion where the heat transfer tube 21 passes through the notch 25K of the baffle plate 25. The concavo-convex portion 21F is not formed.

  Specifically, in the seventh chamber R7, the concavo-convex portion 21F is located at the center portion of the outer peripheral surface of the heat transfer tube 21 that is located between the sixth baffle plate 25f and the seventh baffle plate 25g facing each other. Is formed. On the other hand, in the seventh chamber R7, the uneven portion 21F is not formed in the lower portion and the upper portion other than the central portion, and the outer peripheral surface of the heat transfer tube 21 is smooth.

  In the eighth chamber R8, the concavo-convex portion 21F is formed in the central portion located on the outer peripheral surface of the heat transfer tube 21 while the seventh baffle plate 25g and the eighth baffle plate 25h face each other. On the other hand, in the eighth chamber R8, the uneven portion 21F is not formed in the lower portion and the upper portion other than the central portion, and the outer peripheral surface of the heat transfer tube 21 is smooth.

  In the ninth chamber R <b> 9, the uneven portion 21 </ b> F is between the outer surface of the heat transfer tube 21 and the eighth baffle plate 25 h and the tube plate 23 installed at the other end (left end) of the body 22. It is formed in each of the center part and upper part which are located. On the other hand, in the ninth chamber R9, the uneven portion 21F is not formed in the lower portion other than both the central portion and the upper portion, and the outer peripheral surface of the heat transfer tube 21 is smooth.

[B] Summary As described above, in the supercritical pressure fluid heat exchanger 2 of the present embodiment, the plurality of heat transfer tubes 21 are notched portions of the plurality of baffle plates 25 between the plurality of baffle plates 25. The concavo-convex portion 21F is not formed on the outer surface of the portion that penetrates 25K, and the outer surface is smooth.

  In the supercritical pressure fluid heat exchanger 2 of the present embodiment, the supercritical pressure low boiling point medium M5 is parallel to the tube axis of the heat transfer tube 21 in the portion where the notch portion 25K of the baffle plate 25 is provided. Flowing. For this reason, when the uneven portion 21F is formed on the outer peripheral surface of the heat transfer tube 21 in the portion where the notch portion 25K of the baffle plate 25 is provided, the pressure loss may increase.

  However, in the present embodiment, as described above, in the plurality of heat transfer tubes 21, the concave and convex portions 21F are not formed on the outer surfaces of the portions penetrating the notch portions 25K of the plurality of baffle plates 25, and are smooth. is there.

  Therefore, in this embodiment, an increase in pressure loss can be suppressed.

<Others>
Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 1 ... Heat source medium supply source, 2 ... Supercritical pressure fluid heat exchanger, 3 ... Medium turbine, 3G ... Generator, 4 ... Condenser, 5 ... Supercritical pressure medium pump, 6 ... Cooling water supply part, 21 ... Transmission Heat pipe, 21F ... Uneven portion, 22 ... Body, 23 ... Tube plate, 24 ... Water chamber, 25 ... Baffle plate, 26 ... Heat transfer tube support, 61 ... Cooling water pump, 62 ... Cooler, 63 ... Cooling fan, 261 ... support grid, 262A ... first support plate, 262B ... second support plate

Claims (12)

A supercritical pressure fluid heat exchanger in which heat exchange is performed between a low boiling point medium having a lower boiling point than water and a heat source medium, and the low boiling point medium having the supercritical pressure is heated,
The supercritical fluid heat exchanger is
A plurality of heat transfer tubes in which the heat source medium flows; and a plurality of heat transfer tubes accommodated therein; and a cylinder in which the low-boiling point medium of the supercritical pressure flows around the plurality of heat transfer tubes;
A plurality of baffle plates installed side by side in the cylinder so that the low boiling point medium of supercritical pressure flows meandering from the inlet toward the outlet in the cylinder. ,
The plurality of baffle plates have a distance between one baffle plate and another baffle plate installed next to the one baffle plate so that the low-boiling-point medium of the supercritical pressure inside the cylinder is It is installed to be long along the flow,
Supercritical fluid heat exchanger. Each of the plurality of baffle plates is formed with a notch through which the low boiling point medium of the supercritical pressure passes,
In each of the plurality of baffle plates, the cutout portion is formed so as to increase in area along the flow of the low-boiling-point medium with the supercritical pressure inside the cylinder. ,
The supercritical fluid heat exchanger according to claim 1. A heat transfer tube support portion for supporting the heat transfer tube, provided in a portion located on the outlet side of the low boiling point medium of the supercritical pressure in the cylinder;
The heat transfer tube support portion is installed between one baffle plate of the plurality of baffle plates and another baffle plate installed next to the one baffle plate,
The supercritical fluid heat exchanger according to claim 2. The heat transfer tube support is
Installed inside the barrel, and includes a support plate for supporting the heat transfer tube,
The support plate has the same cutout portion as the cutout portion formed in the one baffle plate among the plurality of baffle plates, and is installed next to the one baffle plate. The same cutout portion as the cutout portion formed in the other baffle plate is formed at the same position,
The supercritical fluid heat exchanger according to claim 3. The heat transfer tube support is
A support grid that is installed inside the barrel and supports the heat transfer tubes;
The support grid is characterized in that a plurality of rod-shaped bodies are arranged along the arrangement of the plurality of heat transfer tubes between the plurality of heat transfer tubes.
The supercritical fluid heat exchanger according to claim 3 or 4. Of the outer surfaces of the plurality of heat transfer tubes, a concavo-convex portion is formed in a portion located on the outlet side of the low boiling point medium of the supercritical pressure,
The supercritical fluid heat exchanger according to any one of claims 1 to 5. In the plurality of heat transfer tubes, the uneven portions are not formed on the outer surface of the portion that penetrates the notch portions of the plurality of baffle plates between the plurality of baffle plates, and the outer surface is smooth. It is characterized by
The supercritical fluid heat exchanger according to claim 6. A fin is formed on the concavo-convex part,
The supercritical fluid heat exchanger according to claim 6 or 7. The plurality of baffle plates have a distance between one baffle plate and another baffle plate installed next to the one baffle plate so that the low-boiling-point medium of the supercritical pressure inside the cylinder is It is different according to the change of density,
The supercritical fluid heat exchanger according to any one of claims 1 to 8. In each of the plurality of baffle plates, the cut-out portion has a different area according to a change in density of the low-boiling-point medium having the supercritical pressure inside the cylinder.
The supercritical fluid heat exchanger according to any one of claims 2 to 9. The supercritical fluid heat exchanger according to any one of claims 1 to 10,
A medium turbine to which a low-boiling medium with a supercritical pressure vaporized by heat exchange in the supercritical fluid heat exchange section is supplied as a working medium.
Power generation system. A supercritical pressure fluid heat exchanger in which heat exchange is performed between a low boiling point medium having a lower boiling point than water and a heat source medium, and the low boiling point medium having the supercritical pressure is heated,
The supercritical fluid heat exchanger is
A plurality of heat transfer tubes in which the heat source medium flows; and a plurality of heat transfer tubes accommodated therein; and a cylinder in which the low-boiling point medium of the supercritical pressure flows around the plurality of heat transfer tubes;
A plurality of baffle plates installed side by side in the cylinder so that the low boiling point medium of supercritical pressure flows meandering from the inlet toward the outlet in the cylinder. ,
The plurality of baffle plates are arranged such that a distance between one baffle plate and another baffle plate installed next to the one baffle plate is greater than the inlet side of the low-boiling-point medium having the supercritical pressure. It is characterized by being installed to be long in
Supercritical fluid heat exchanger.

Images