JP2017190682A - Ejector and fluid circulation system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an ejector which can improve the operation efficiency of a fluid circulation system having at least two routes in which a driven fluid flows when employed for the fluid circulation system, and a fluid circulation system using the ejector.SOLUTION: An ejector 10 comprises: a case 100 in which a space is formed; a nozzle 300 for injecting a drive fluid from an injection port 320; and a first suction part 210 and a second suction part 220 for introducing a sucked driven fluid into the case 100. A first suction port 211 being an outlet of the driven fluid is formed at a downstream-side end part of the first suction part 210, and a second suction port 221 being an outlet of the driven fluid is formed at a downstream-side end part of the second suction part 220. The first suction port 211 and the second suction port 221 are formed at positions whose coordinates in a direction in which the drive fluid flows differ from each other.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an ejector that sucks a driven fluid by using a flow of a driving fluid, and a fluid circulation system using the ejector.

  The ejector is a fluid pump that converts the expansion energy of the driving fluid ejected from the nozzle into kinetic energy and sucks the driven fluid by the suction action. Ejectors are widely used in fluid circulation systems that circulate fluid, such as refrigeration cycles and fuel cell systems. For example, in the refrigeration cycle described in Patent Document 1 below, an ejector is used as a device for sucking the refrigerant discharged from the evaporator by using the flow of the refrigerant discharged from the condenser.

  In such a configuration, the refrigerant discharged from the condenser corresponds to the driving fluid, and the refrigerant discharged from the evaporator corresponds to the driven fluid. Moreover, the ejector in the above configuration also functions as an expansion valve for decompressing the refrigerant on the upstream side of the evaporator. In the refrigeration cycle having such a configuration, since the operation of the compressor is assisted by the ejector, the operation load of the compressor is reduced. As a result, the operating efficiency of the refrigeration cycle can be increased.

  The refrigeration cycle described in Patent Document 1 below includes an evaporator having a high evaporation temperature (hereinafter also referred to as “high temperature evaporator”) and an evaporator having a low evaporation temperature (hereinafter also referred to as “low temperature evaporator”). It has. The flow of the refrigerant discharged from the high-temperature evaporator and the flow of the refrigerant discharged from the low-temperature evaporator merge to form one flow, and are then sucked into the ejector as a driven fluid. Thus, in the fluid circulation system, there may be two or more paths through which the driven fluid flows.

  In the refrigeration cycle described in Patent Document 1 below, the refrigerant flow path is branched into two in the upstream portion of the high temperature evaporator and the low temperature evaporator. Further, a throttle as a pressure loss generating means is provided between the branch point and the low temperature evaporator. For this reason, the pressure of the refrigerant | coolant supplied to a low-temperature evaporator becomes low, and, thereby, the temperature of the refrigerant | coolant in a low-temperature evaporator becomes low.

JP 2005-249315 A

  In the refrigeration cycle described in Patent Document 1, the refrigerant discharged from the high-temperature evaporator and the refrigerant discharged from the low-temperature evaporator are left as they are before being sucked into the ejector (one is not decompressed). It is configured to merge. For this reason, it is considered that the pressure difference between the refrigerant inside the high temperature evaporator and the refrigerant inside the low temperature evaporator is relatively small. In order to increase this pressure difference and increase the temperature difference between the high-temperature evaporator and the low-temperature evaporator, an additional point is provided at a position downstream of the high-temperature evaporator and upstream of the above-mentioned junction. It is possible to arrange an aperture.

  However, when the throttle is arranged at the above position, the expansion work when the refrigerant passes through the throttle is wasted. In this case, the specific enthalpy when the refrigerant, which is the driven fluid, is sucked into the ejector increases and the pressurization performance by the ejector decreases, so that the operating efficiency of the refrigeration cycle cannot be sufficiently improved.

  As described above, in the fluid circulation system in which there are at least two paths through which the driven fluid flows and the pressures of the fluids in the respective paths are different from each other, there is room for further improving the operation efficiency. .

  The present invention has been made in view of the above problems, and its object is to improve the operation efficiency of the fluid circulation system when used in a fluid circulation system in which at least two paths through which the driven fluid flows exist. It is an object of the present invention to provide an ejector that can be improved, and a fluid circulation system using the ejector.

  In order to solve the above problems, an ejector according to the present invention is an ejector (10, 10A, 10B, 10C) for sucking a driven fluid using a flow of a driving fluid, and a space is formed therein. The case (100), the nozzle (300) for ejecting the driving fluid from the ejection port (320) inside the case, the first suction part (210) and the second suction unit for guiding the driven fluid to be sucked into the case A suction part (220). A first suction port (211) that is an outlet of the driven fluid is formed at the downstream end of the first suction portion, and an outlet of the driven fluid is formed at the downstream end of the second suction portion. A second suction port (221) is formed. Inside the case, the first suction port and the second suction port are formed at different positions in the direction in which the driving fluid flows.

  When the ejector having such a configuration is operating, that is, when the driving fluid is ejected from the nozzle, the pressure distribution in the case is not uniform. Specifically, the pressure inside the case changes depending on the position (coordinates) in the direction in which the driving fluid flows. For this reason, by appropriately designing the internal structure of the ejector, the pressure at the position of the first suction port and the pressure at the position of the second suction port can be made different from each other. For example, the ejector can be configured so that the pressure at the position of the second suction port is lower than the pressure at the second suction port.

  When an ejector having such a configuration is used in a fluid circulation system in which at least two paths through which the driven fluid flows exist, each path is connected to the ejector without previously merging the two driven fluid flows. can do. Of the paths through which the driven fluid flows, a path having a lower pressure is a "low pressure side path" and a path having a higher pressure is a "high pressure side path". It is desirable to connect the downstream end of the low pressure side path to the second suction part.

  In this case, the pressure difference between the high-pressure side path and the low-pressure side path is absorbed by the existing pressure difference inside the ejector. Therefore, the pressure difference between the high pressure side path and the low pressure side path can be maintained without providing a throttle in the middle of the high pressure side path. Since the expansion work when the driven fluid passes through the throttle, that is, the energy that should have been wasted in the throttle, is recovered, the boosting performance of the ejector is improved. As a result, the operation efficiency of the fluid circulation system using the ejector is also improved.

  The driven fluid sucked from the first suction unit and the driven fluid sucked from the second suction unit may be the same type of fluid or different types of fluids. Further, at least one of the two may be the same type of fluid as the driving fluid, or may be a different type of fluid.

  According to the present invention, when used in a fluid circulation system having at least two paths through which a driven fluid flows, an ejector capable of improving the operation efficiency of the fluid circulation system, and a fluid circulation using the ejector A system is provided.

It is a figure which shows the structure of the ejector which concerns on 1st Embodiment of this invention. It is a figure which shows the pressure distribution in the inside of an ejector. It is a figure which shows the structure of the refrigerating cycle using the ejector of FIG. It is a Mollier diagram which shows the state of the refrigerant | coolant in each part of the refrigerating cycle of FIG. It is a figure which shows the structure of the ejector which concerns on 2nd Embodiment of this invention. It is a figure which shows the structure of the ejector which concerns on 3rd Embodiment of this invention. It is a figure which shows the structure of the ejector which concerns on 4th Embodiment of this invention. It is a figure which shows the structure of the fuel cell system using the ejector of FIG. It is a figure which shows the structure of the ejector which concerns on the comparative example of this invention, and a refrigerating cycle using the same. FIG. 10 is a Mollier diagram showing the state of the refrigerant in each part of the refrigeration cycle in FIG. 9.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. In order to facilitate the understanding of the description, the same constituent elements in the drawings will be denoted by the same reference numerals as much as possible, and redundant description will be omitted.

  A first embodiment of the present invention will be described with reference to FIG. The ejector 10 according to the first embodiment functions as a fluid pump that sucks the driven fluid using the flow of the driving fluid. The ejector 10 includes a case 100, a nozzle 300, a first suction unit 210, and a second suction unit 220.

  The case 100 is a cylindrical member having a space formed therein. The space is formed as a straight channel. In FIG. 1, the direction in which the fluid flows in the space inside the case 100 is indicated by a dotted arrow DL1. The case 100 has a circular cross section perpendicular to the fluid flow direction. However, the diameters (inner diameter and outer diameter of the cross section) are different in each part along the direction. An end of the case 100 on the upstream side (left side in FIG. 1) is closed by a wall 111. A discharge port 131 serving as a fluid outlet is formed at the end of the case 100 on the downstream side (right side in FIG. 1).

  The case 100 has a main body part 110, a mixing part 120, and a diffuser part 130, which are formed so as to be integrated. The main body 110 is the most upstream part of the case 100. A portion of the main body 110 on the side of the mixing unit 120 is formed in a taper shape, and its inner diameter becomes smaller toward the downstream side. As will be described later, the main body 110 in this embodiment is a part that receives the driven fluid sucked into the ejector 10 through the first suction part 210 and the second suction part 220.

  The mixing unit 120 is a part on the downstream side of the main body part 110 in the case 100 and is a part on the upstream side of the diffuser part 130. The mixing part 120 has a cylindrical shape, and its inner diameter is substantially constant regardless of the position. As will be described later, the mixing unit 120 is a part that flows while the driving fluid and the driven fluid are mixed.

  The diffuser portion 130 is the most downstream portion of the case 100. The diffuser portion 130 is formed in a tapered shape, and its inner diameter increases toward the downstream side. As will be described later, the diffuser portion 130 is a portion where the fluid (driving fluid and driven fluid) that has passed through the mixing portion 120 flows while increasing its pressure. As described above, the outlet 131 is formed at the downstream end of the diffuser portion 130.

  The nozzle 300 is a member for ejecting driving fluid inside the case 100. The nozzle 300 has a substantially cylindrical shape, and a linear space is formed therein. The space is a flow path through which the driving fluid flows. The central axis of the nozzle 300 coincides with the central axis of the case 100. The nozzle 300 is fixed to the case 100 in a state of vertically penetrating the wall 111 of the case 100.

  An upstream end of the nozzle 300 protrudes toward the outside of the case 100. A supply port 310 serving as an inlet for driving fluid is formed at the end. A portion of the nozzle 300 near the end on the downstream side is formed in a taper shape, and the inner diameter becomes smaller toward the downstream side. At the downstream end of the nozzle 300, an injection port 320 that is an outlet of the driving fluid is formed. The driving fluid supplied from the supply port 310 to the nozzle 300 flows through the nozzle 300 while increasing the flow velocity, and is then injected from the injection port 320 inside the case 100. The direction in which the driving fluid flows and is ejected is the same as the direction in which the fluid flows through the mixing unit 120 and the diffuser unit 130, that is, the direction indicated by the arrow DL1 in FIG. Hereinafter, this direction is also referred to as “injection direction”.

  The first suction part 210 is a cylindrical pipe, and one end thereof is connected to the side wall 112 of the main body part 110 in the case 100. The internal space of the first suction part 210 and the internal space of the main body part 110 are connected. The first suction part 210 is a part for guiding the driven fluid sucked by the ejector 10 to the inside of the case 100. The central axis of the first suction unit 210 intersects the central axis of the case 100 perpendicularly. In the present embodiment, the first suction part 210 is formed integrally with the case 100. A first suction port 211 that is an outlet of the driven fluid is formed at the downstream end of the first suction unit 210, that is, at a connection portion between the first suction unit 210 and the side wall 112.

  The second suction part 220 is a cylindrical pipe, and one end of the second suction part 220 is connected to the side wall 112 of the main body 110 in the case 100. The position where the second suction part 220 is connected to the side wall 112 is on the downstream side in the ejection direction from the position where the first suction part 210 is connected to the side wall 112.

  The internal space of the second suction part 220 and the internal space of the main body part 110 are connected. Similar to the first suction part 210, the second suction part 220 is a part for guiding the driven fluid sucked by the ejector 10 to the inside of the case 100. The central axis of the second suction unit 220 intersects the central axis of the case 100 perpendicularly. In the present embodiment, the second suction part 220 is formed integrally with the case 100. A second suction port 221 that is an outlet of the driven fluid is formed at a downstream end of the second suction unit 220, that is, a connection portion between the second suction unit 220 and the side wall 112.

  When the ejector 10 is viewed along the injection direction, the angle formed by the central axis of the first suction unit 210 and the central axis of the second suction unit 220 may be 0 degrees or any other angle. It may be.

  When the driving fluid is ejected from the ejection port 320 of the nozzle 300, the pressure inside the case 100 decreases due to the flow of the driving fluid. Accordingly, the driven fluid is sucked from each of the first suction unit 210 and the second suction unit 220 and flows into the main body 110. Each sucked driven fluid merges with the driving fluid in the mixing unit 120 and flows toward the downstream side while being mixed with the driving fluid. At that time, the pressure of the mixed fluid gradually increases toward the downstream side. The mixed fluid flows through the diffuser portion 130 while continuing to increase the pressure, and is then discharged from the discharge port 131 to the outside.

  The pressure distribution inside the case 100 will be described with reference to FIG. The graph shown in the lower part of FIG. 2 shows the pressure distribution inside the case 100 when the driving fluid is ejected from the nozzle 300. The horizontal axis of FIG. 2 shows the coordinates in the direction in which the driving fluid flows, that is, the injection direction indicated by the dotted line DL1. Hereinafter, the coordinates may be referred to as “x coordinates”.

  In FIG. 2, the x coordinate of the first suction port 211 is shown as x1, the x coordinate of the second suction port 221 is shown as x2, and the x coordinate of the ejection port 320 is shown as x3. Thus, the first suction port 211 and the second suction port 221 in the present embodiment are formed at different positions in the direction in which the driving fluid flows. In FIG. 2, the x coordinate at the downstream end of the mixing unit 120 is shown as x4, and the x coordinate of the discharge port 131 is shown as x5.

  A line PL1 in FIG. 2 is a graph showing the pressure distribution on the central axis of the case 100. Accordingly, the portion of the line PL1 on the upstream side (left side) of x3 indicates the pressure distribution of the driving fluid inside the nozzle 300. Further, the portion of the line PL1 on the downstream side (right side) from x3 indicates the pressure distribution of the mixed fluid in the mixing unit 120 and the diffuser unit 130.

  A line PL2 in FIG. 2 indicates the pressure distribution in the space around the nozzle 300 in the main body 110.

  As indicated by the line PL1, the pressure (P4) inside the nozzle 300 is relatively high as the driving fluid is supplied from the outside. The pressure of the driving fluid gradually decreases as it approaches the injection port 320, and becomes the lowest pressure (P1) at a position immediately after being injected from the injection port 320.

  As indicated by the line PL2, the pressure on the upstream side of the main body 110, that is, in the vicinity of the wall 111 is lower than the pressure (P4) in the nozzle 300 and is higher than the pressure (P1) in the vicinity of the injection port 320. Is also expensive. However, as it approaches the injection port 320, the pressure in the main body 110 becomes lower due to the influence of the flow of the injected driving fluid. The line PL2 and the line PL1 overlap each other on the downstream side from the position where the x coordinate is x3.

  As already described, in the portion on the downstream side of x3, the mixed fluid of the driving fluid and the driven fluid flows while being pressurized as it goes downstream. For this reason, in the case 100, the pressure is the lowest at the position (x3) of the injection port 320. That is, the pressure in the case 100 increases as the distance from the injection port 320 increases toward the upstream side or the downstream side.

  In the present embodiment, the distance from the ejection port 320 to the second suction port 221 in the direction in which the driving fluid flows (the ejection direction of the arrow DL1) is shorter than the distance from the ejection port 320 to the first suction port 211 in the same direction. It has become. When the driving fluid is ejected from the nozzle 300, the pressure distribution as shown in FIG. As a result, the pressure (P2) at the position (x2) of the second suction port 221 is lower than the pressure (P3) at the position (x1) of the first suction port 211. In other words, the positions of the first suction unit 210 and the second suction unit 220 are determined so that a pressure difference is generated between the first suction port 211 and the second suction port 221. . The effect of generating such a pressure difference will be described later.

  An example of a fluid circulation system using the ejector 10 will be described with reference to FIG. FIG. 3 schematically shows the configuration of a refrigeration cycle 400 used in, for example, a vehicle air conditioner. In addition to the ejector 10, the refrigeration cycle 400 includes a compressor 410, a condenser 420, a first evaporator 431, a second evaporator 432, and a gas-liquid separator 440.

  The compressor 410 is a device for compressing the refrigerant and sending it out to the condenser 420 side, thereby circulating the refrigerant in the refrigeration cycle 400. The compressor 410 operates by receiving power supply from the outside. Therefore, as the operating load of the compressor 410 increases, the compressor 410 consumes more power (energy). In order to improve the operating efficiency of the refrigeration cycle, it is desirable to keep the operating load of the compressor 410 as small as possible.

  The refrigerant sent out from the compressor 410 is supplied to the condenser 420 through the pipe 401. The condenser 420 is a heat exchanger for causing heat exchange between the refrigerant and the air that has reached a high temperature in the compressor 410 to condense the refrigerant. The refrigerant condenses when passing through the condenser 420 and changes from the gas phase to the liquid phase. Thereafter, the refrigerant is supplied to the supply port 310 of the ejector 10 through the pipe 402. That is, in the present embodiment, the refrigerant discharged from the condenser 420 is jetted from the nozzle 300 as a driving fluid. At that time, as shown in FIG. 2, the pressure of the refrigerant greatly decreases from P4 to P1. In the refrigeration cycle 400, the ejector 10 functions as a so-called “expansion valve”.

  The refrigerant jetted from the nozzle 300 is boosted inside the ejector 10 together with the refrigerant sucked from the first evaporator 431 and the like, and is discharged from the discharge port 131. Thereafter, the refrigerant is supplied to the gas-liquid separator 440 through the pipe 403.

  The gas-liquid separator 440 is a container provided to separate a gas-phase refrigerant and a liquid-phase refrigerant inside. The upper portion of the gas-liquid separator 440 and the compressor 410 are connected by a pipe 404. For this reason, only the gas phase refrigerant out of the refrigerant discharged from the ejector 10 is sucked into the compressor 410 and flows again toward the condenser 420.

  One end of a pipe 405 is connected to the lower part of the gas-liquid separator 440. The other end side of the pipe 405 branches into a pipe 406 and a pipe 407. The pipe 406 is a pipe for supplying the liquid-phase refrigerant discharged from the gas-liquid separator 440 to the first evaporator 431. The pipe 407 is a pipe for supplying the liquid-phase refrigerant discharged from the gas-liquid separator 440 to the second evaporator 432.

  The first evaporator 431 is a heat exchanger for causing heat exchange between the low-pressure refrigerant supplied from the ejector 10 via the gas-liquid separator 440 and the air and evaporating the refrigerant. The refrigerant evaporates when passing through the first evaporator 431 and changes from the liquid phase to the gas phase. Thereafter, the refrigerant is sucked into the first suction part 210 of the ejector 10 through the pipe 408. That is, in the present embodiment, the refrigerant discharged from the first evaporator 431 is sucked as the driven fluid in the first suction unit 210. The pipe 408 corresponds to a “first flow path” through which the driven fluid flows, and its downstream end is connected to the first suction unit 210.

  Similar to the first evaporator 431, the second evaporator 432 also exchanges heat between the low-pressure refrigerant supplied from the ejector 10 via the gas-liquid separator 440 and the air, and evaporates the refrigerant. It is comprised as a heat exchanger for making it. The refrigerant evaporates when passing through the second evaporator 432 and changes from the liquid phase to the gas phase. Thereafter, the refrigerant is sucked into the second suction part 220 of the ejector 10 through the pipe 409. That is, in the present embodiment, the refrigerant discharged from the second evaporator 432 is sucked as the driven fluid in the second suction unit 220. The pipe 409 corresponds to a “second flow path” through which the driven fluid flows, and its downstream end is connected to the second suction unit 220.

  A diaphragm 411 is provided in the middle of the pipe 405. A throttle 412 is provided in the middle of the pipe 407. The refrigerant reduces its pressure when passing through the respective throttles. For this reason, when the refrigeration cycle 400 is operating, the refrigerant pressure inside the second evaporator 432 is lower than the refrigerant pressure inside the first evaporator 431. As a result, the temperature of the refrigerant inside the second evaporator 432 is lower than the temperature of the refrigerant inside the first evaporator 431.

  With such a configuration, the temperature of the air that has passed through the first evaporator 431 and the temperature of the air that has passed through the second evaporator 432 can be made different. For this reason, the air conditioner provided with the refrigeration cycle 400 can simultaneously perform cooling in each of the plurality of cooling target spaces at different set temperatures.

  By providing the throttle 412, the refrigerant pressure inside the pipe 409 is lower than the refrigerant pressure inside the pipe 408. In the present embodiment, the low-pressure side pipe 408 is connected to the second suction part 220 having a low pressure (P2) as shown in FIG. Further, the high-pressure side pipe 409 is connected to the first suction part 210 having a high pressure (P3) as shown in FIG. For this reason, the refrigerant pressure difference between the first evaporator 431 and the second evaporator 432 is maintained even though the throttle is not provided in the middle of the pipe 408.

  The state of the refrigerant in each part when the refrigeration cycle 400 is operating will be described with reference to FIG. FIG. 4 is a so-called Mollier diagram, in which the horizontal axis represents the specific enthalpy of the refrigerant, and the vertical axis represents the pressure of the refrigerant. A dotted line L1 drawn on the left side of the critical point CP is a saturated liquid line, and a dotted line L2 drawn on the right side of the critical point CP is a saturated vapor line. Hereinafter, they are denoted as “saturated liquid line L1” and “saturated vapor line L2”, respectively.

  In FIG. 4, state points representing the state of the refrigerant in each part of the refrigeration cycle 400 are shown as state points S01 to S12. The state point S01 represents the state of the refrigerant immediately before it is discharged from the compressor 410 and flows into the condenser 420. The state point S02 represents the state of the refrigerant immediately after being discharged from the condenser 420. When shifting from the state point S01 to the state point S02, the specific enthalpy decreases as the refrigerant is condensed.

  The state point S03 represents the state of the refrigerant immediately before being injected from the injection port 320 in the nozzle 300. When shifting from the state point S02 to the state point S03, the refrigerant pressure and specific enthalpy decrease as the expansion energy of the refrigerant is converted into kinetic energy.

  The state point S04 represents the state of the refrigerant in the mixing unit 120. The refrigerant is a refrigerant immediately after the refrigerant (driving fluid) ejected from the ejection port 320 and the refrigerant (driven fluid) discharged from the first evaporator 431 and the second evaporator 432 are mixed. The change from the state point S03 to the state point S04 is caused by the mixing of the driving fluid and the driven fluid as described above.

  The state point S05 represents the state of the refrigerant at the outlet of the ejector 10, that is, the discharge port 131. When shifting from the state point S04 to the state point S05, the pressure of the refrigerant is increased by increasing the pressure inside the ejector 10. Along with this, the specific enthalpy of the refrigerant has also increased.

  The state point S06 represents the state of the refrigerant just before being sucked into the compressor 410. The refrigerant indicated by the state point S06 is a gas-phase refrigerant immediately after passing through the gas-liquid separator 440 from the gas-liquid mixing state. Therefore, the state point S06 is a state point on the saturated vapor line L2. When the refrigerant is compressed by the compressor 410, the refrigerant state shifts from the state point S06 to the state point S01. At that time, the pressure of the refrigerant and the specific enthalpy both increase as it is compressed.

  The state point S07 represents the state of the refrigerant between the gas-liquid separator 440 and the throttle 411. The refrigerant indicated by the state point S07 is a liquid-phase refrigerant immediately after passing through the gas-liquid separator 440 from the gas-liquid mixing state. Therefore, the state point S07 is a state point on the saturated liquid line L1.

  The state point S08 represents the state of the refrigerant immediately after passing through the aperture 411. Changes in the potential energy and kinetic energy of the refrigerant when passing through the diaphragm 411 are negligible. Accordingly, when the state point S07 is shifted to the state point S08, only the refrigerant pressure is decreased, and the specific enthalpy of the refrigerant hardly changes.

  State point S09 represents the state of the refrigerant immediately after passing through the throttle 412. Changes in the potential energy and kinetic energy of the refrigerant when passing through the diaphragm 412 are negligible. Therefore, even when the state point S08 shifts to the state point S09, only the refrigerant pressure decreases, and the specific enthalpy of the refrigerant hardly changes.

  The state point S10 represents the state of the refrigerant immediately after being discharged from the first evaporator 431. When shifting from the state point S08 to the state point S10, the specific enthalpy increases as the refrigerant evaporates. At that time, the pressure of the refrigerant slightly decreases. The refrigerant discharged from the first evaporator 431 is sucked into the ejector 10 from the first suction unit 210. Thereafter, the inside of the main body 110 is moved from the first suction port 211 on the high pressure side toward the second suction port 221 on the low pressure side. The state point S12 represents the state of the refrigerant when the refrigerant moving in this way reaches the position of the second suction port 221. When shifting from the state point S10 to the state point S12, the state of the refrigerant changes along the isentropic line L3. At that time, the specific enthalpy of the refrigerant decreases.

  The refrigerant that has moved from the first suction port 211 to the second suction port 221 merges with the coolant from the nozzle 300 that is the driving fluid. As a result, the state point indicating the state of the refrigerant moves from the state point S12 to the state point S04.

  The state point S11 represents the state of the refrigerant immediately after being discharged from the second evaporator 432. When shifting from the state point S09 to the state point S11, the specific enthalpy increases as the refrigerant evaporates. At that time, the pressure of the refrigerant slightly decreases. The refrigerant discharged from the second evaporator 432 is sucked into the ejector 10 from the second suction unit 220 and then merged with the refrigerant from the nozzle 300 that is the driving fluid. As a result, the state point indicating the state of the refrigerant moves from the state point S11 to the state point S04.

  As described above, in the refrigeration cycle 400 according to the present embodiment, the first fluid (pipe 406 and the pipe 408) passing through the first evaporator 431 and the second evaporator 432 are passed as the flow path of the driven fluid. And a second path (a pipe 407 and a pipe 409). Of these, the refrigerant pressure inside the second path is lower than the refrigerant pressure inside the first path. The downstream end portion of the second path is connected to the second suction portion 220 on the low pressure side. Further, the downstream end portion of the first path is connected to the first suction portion 210 on the high pressure side.

  In order to explain the effect of such a configuration, a refrigeration cycle 400D according to a comparative example will be described. FIG. 9 shows the configuration of the refrigeration cycle 400D. Of the refrigeration cycle 400D, the same components as those in the refrigeration cycle 400 are denoted by the same reference numerals as those shown in FIG.

  The ejector 10D provided in the refrigeration cycle 400D is obtained by eliminating the first suction unit 210 from the ejector 10 shown in FIG. That is, the ejector 10D is configured to have only one portion (second suction portion 220) for sucking the driven fluid, like the conventional ejector. The other configuration of the ejector 10D is the same as the configuration of the ejector 10.

  In the refrigeration cycle 400D, the downstream end of the pipe 408 and the downstream end of the pipe 409 are connected to one end of the pipe 409D. The other end side of the pipe 409D is connected to the second suction part 220 of the ejector 10D. As described above, the refrigeration cycle 400D has a configuration in which the refrigerant discharged from the first evaporator 431 and the refrigerant discharged from the second evaporator 432 join together in advance and then are sucked into the ejector 10D.

  A diaphragm 413 is provided in the middle of the pipe 408. Thereby, the pressure difference (and the resulting temperature difference) between the refrigerant inside the first evaporator 431 and the refrigerant inside the second evaporator 432 is maintained.

  The state of the refrigerant in each part when the refrigeration cycle 400D is operating will be described with reference to FIG. FIG. 10 is a Mollier diagram drawn similarly to FIG. The meanings of symbols such as “S01” shown in FIG. 10 are substantially the same as the meanings of the symbols shown in FIG. For example, the state point S01 in FIG. 10 represents the state of the refrigerant just before being discharged from the compressor 410 of the refrigeration cycle 400D and flowing into the condenser 420. However, even if the state points have the same reference numerals, the refrigerant pressure and the specific enthalpy indicated by the respective state points may be different from each other. In the following, only the parts different from FIG. 4 will be described, and description of parts common to FIG. 4 will be omitted as appropriate.

  In the refrigeration cycle 400D, the refrigerant (state point S10) immediately after passing through the first evaporator 431 is sucked into the ejector 10D after further reducing its pressure by passing through the throttle 413. When the refrigerant passes through the throttle 413, the state of the refrigerant changes from the state point S10 to the state point S12.

  At this time, the specific enthalpy of the refrigerant hardly changes, for example, as in the case of transition from the state point S07 to the state point S08. As a result, the specific enthalpy of the refrigerant immediately before being sucked into the ejector 10D is larger than when the state of the refrigerant changes along the isentropic line (as shown in FIG. 4). That is, the specific enthalpy of the refrigerant represented by the state point S12 in FIG. 10 is larger than the specific enthalpy of the refrigerant represented by the state point S12 in FIG. This is because part of the kinetic energy has changed to thermal energy due to the disturbance of the refrigerant flow immediately after passing through the throttle 413. In other words, in the refrigeration cycle 400D, the expansion work of the refrigerant (the difference in the specific enthalpy as described above) when passing through the throttle 413 is wasted.

  As a result, in FIG. 10, the specific enthalpy indicated by the state point S04 is larger than that in FIG. As a result, the amount of pressure increase inside the ejector 10D is smaller than the amount of pressure increase inside the ejector 10. Therefore, the refrigerant pressure indicated by the state point S05 in FIG. 10 is lower than the refrigerant pressure indicated by the state point S05 in FIG.

  In order to make the refrigeration cycle 400D function in the same manner as in the example shown in FIG. 4, the refrigerant discharged from the ejector 10D (state point S05) is compressed by the compressor 410 until the pressure indicated by the state point S01 is reached. Must be compressed. Note that the pressure indicated by the state point S01 in FIG. 10 is the same as the pressure indicated by the state point S01 in FIG.

  The power necessary to compress the refrigerant and shift from the state point S05 to the state point S01 is greater in the example of FIG. 10 than in the example of FIG. That is, in the refrigeration cycle 400D, the operating load on the compressor 410 increases as a result of the restriction 413 being provided to maintain the pressure difference between the first evaporator 431 and the second evaporator 432. ing.

  On the other hand, in the refrigeration cycle 400 shown in FIGS. 3 and 4, the refrigerant between the first evaporator 431 and the second evaporator 432 is configured such that the throttle 413 is not provided in the middle of the pipe 408. The pressure difference is maintained. As described with reference to FIGS. 2 to 4, the pressure difference is realized by using an existing pressure distribution generated inside the ejector 10.

  Further, in the refrigeration cycle 400, the use of the ejector 10 having the configuration shown in FIG. 2 does not cause expansion work that is wasted on the downstream side of the first evaporator 431. Since the operation load of the compressor 410 is reduced, the operation efficiency of the refrigeration cycle 400 is improved when compared with the refrigeration cycle 400D having the configuration shown in FIG.

  In the refrigeration cycle 400, there are two paths through which the driven fluid flows. Instead of such a mode, a mode in which there are three or more paths through which the driven fluid flows may be used. In that case, the ejector 10 is provided with the same number of suction parts (corresponding to the first suction part 210 and the second suction part 220) as the number of paths through which the driven fluid flows. In addition, the connection destination (suction part) of each path to the ejector 10 is determined according to the magnitude of the pressure in each path through which the driven fluid flows and the pressure distribution inside the ejector 10.

  A second embodiment of the present invention will be described with reference to FIG. The ejector 10A according to the second embodiment differs from the first embodiment in the position where the first suction part 210 is provided and the position where the second suction part 220 is provided. Other points are the same as those of the first embodiment.

  In the present embodiment, the first suction unit 210 and the second suction unit 220 are not connected to the side wall 112 of the main body 110, but are both connected to the mixing unit 120. In FIG. 5, the x coordinate of the first suction port 211 is shown as x11, and the x coordinate of the second suction port 221 is shown as x12. Both x11 and x12 are coordinates closer to the discharge port 131 than the x coordinate (x3) of the injection port 320.

  In the ejector 10 according to the first embodiment, both the first suction port 211 and the second suction port 221 are formed at positions upstream of the ejection port 320 in the direction in which the driving fluid flows (injection direction). It had been. On the other hand, in the ejector 10A according to the second embodiment, both the first suction port 211 and the second suction port 221 are formed at a position downstream of the ejection port 320 in the direction in which the driving fluid flows. Has been.

  Also in this embodiment, the distance from the ejection port 320 to the second suction port 221 in the direction in which the driving fluid flows (the ejection direction of the arrow DL1) is shorter than the distance from the ejection port 320 to the first suction port 211 in the same direction. It has become. Therefore, as apparent from the graph shown in the lower part of FIG. 2, when the driving fluid is ejected from the nozzle 300, the pressure at the position (x12) of the second suction port 221 is the first suction port. The pressure is lower than the pressure at the position 211 (x11). Therefore, in the refrigeration cycle 400 of FIG. 3, even when the ejector 10 is replaced with the ejector 10A, the same effect as described above can be obtained.

  A third embodiment of the present invention will be described with reference to FIG. The ejector 10B according to the third embodiment is different from the first embodiment in the position where the first suction part 210 is provided and the position where the second suction part 220 is provided. Other points are the same as those of the first embodiment.

  In the present embodiment, the second suction part 220 is connected to the mixing part 120 instead of the side wall 112 of the main body part 110. The first suction part 210 is also connected to the side wall 112 of the main body part 110 in this embodiment. However, as the connection position of the second suction part 220 is changed as described above, the connection position of the first suction part 210 is slightly discharged from the position of the first suction part 210 shown in FIG. The position is closer to the exit 131 side.

  In FIG. 6, the x coordinate of the first suction port 211 is shown as x21, and the x coordinate of the second suction port 221 is shown as x22. x21 is a coordinate closer to the wall 111 than the x coordinate (x3) of the injection port 320. x22 is a coordinate closer to the discharge port 131 than the x coordinate (x3) of the ejection port 320.

  That is, in the ejector 10B according to the third embodiment, the first suction port 211 is formed at a position upstream of the injection port 320 in the direction in which the driving fluid flows (the injection direction of the arrow DL1). A second suction port 221 is formed at a position downstream of 320. Further, the distance from the ejection port 320 to the second suction port 221 in the direction in which the driving fluid flows is shorter than the distance from the ejection port 320 to the first suction port 211 in the same direction. Therefore, as apparent from the graph shown in the lower part of FIG. 2, when the driving fluid is ejected from the nozzle 300, the pressure at the position (x22) of the second suction port 221 is the first suction port. The pressure is lower than the pressure at the position 211 (x21). Therefore, in the refrigeration cycle 400 of FIG. 3, even when the ejector 10 is replaced with the ejector 10B, the same effect as described above is obtained.

  Even if the distance from the ejection port 320 to the second suction port 221 in the direction in which the driving fluid flows is longer than the distance from the ejection port 320 to the first suction port 211 in the same direction. Good. In this case, the function of the first suction unit 210 and the function of the second suction unit 220 are interchanged. That is, the pipe 409 from the second evaporator 432 is connected to the first suction part 210, and the pipe 408 from the first evaporator 431 is connected to the second suction part 220.

  A fourth embodiment of the present invention will be described with reference to FIG. The ejector 10 </ b> C according to the fourth embodiment is different from the first embodiment in the configurations of the first suction unit 210 and the second suction unit 220. Other points are the same as those of the first embodiment.

  In the present embodiment, the first suction part 210 is formed as a cylindrical member, and is fixed to the case 100 through the wall 111 of the main body part 110. The central axis of the first suction part 210 is parallel to the central axis of the case 100. Therefore, the direction in which the driven fluid flows through the first suction unit 210 (the first direction indicated by the arrow AR1) is the same direction as the direction in which the driving fluid is ejected from the nozzle 300.

  The same applies to the second suction unit 220. The second suction part 220 is formed as a cylindrical member, and is fixed to the case 100 through the wall 111 of the main body part 110. The central axis of the second suction part 220 is parallel to the central axis of the case 100. Therefore, the direction in which the driven fluid flows through the second suction unit 220 (the second direction indicated by the arrow AR2) is the same direction as the direction in which the driving fluid is ejected from the nozzle 300.

  The first suction part 210 and the second suction part 220 are different from each other in the length of the portion disposed inside the main body part 110. In FIG. 7, the x coordinate of the first suction port 211 is shown as x31, and the x coordinate of the second suction port 221 is shown as x32. Both x31 and x32 are coordinates closer to the wall 111 than the x coordinate (x3) of the injection port 320.

  In the present embodiment, the second suction part 220 extends further toward the downstream side (the discharge port 131 side) than the first suction part 210. For this reason, the distance from the ejection port 320 to the second suction port 221 in the direction in which the driving fluid flows (the ejection direction of the arrow DL1) is shorter than the distance from the ejection port 320 to the first suction port 211 in the same direction. Yes.

  Therefore, as apparent from the graph shown in the lower part of FIG. 2, when the driving fluid is ejected from the nozzle 300, the pressure at the position (x32) of the second suction port 221 is the first suction port. The pressure is lower than the pressure at the position 211 (x31). Therefore, in the refrigeration cycle 400 of FIG. 3, even when the ejector 10 is replaced with the ejector 10C, the same effect as described above can be obtained.

  Further, in the ejector 10C, the direction in which the driving fluid flows and the direction in which the driven fluid flows are substantially parallel. Since the collision between the driving fluid and the driven fluid is difficult to occur, the phenomenon that the flow of the fluid is disturbed and a part of kinetic energy is changed to thermal energy is suppressed. As a result, it is possible to efficiently increase the pressure of the fluid in the ejector 10C.

  It should be noted that the central axis of only one of the first suction part 210 and the second suction part 220 may be parallel to the central axis of the case 100. That is, only one of the first suction unit 210 and the second suction unit 220 may be configured as shown in FIG. 7, and the other may be configured as shown in FIG.

  The ejector 10 and the like can also be used in a fluid circulation system other than the refrigeration cycle shown in FIG. FIG. 8 shows a fuel cell system 500 as another example of the fluid circulation system using the ejector 10. In addition to the ejector 10, the fuel cell system 500 includes a cell stack 510, a combustor 530, and a reformer 520.

  The cell stack 510 is an aggregate of a plurality of single cells (not shown). Each unit cell is a solid oxide fuel cell (SOFC), in which a fuel electrode (anode) is formed on one side of a flat solid electrolyte, and on the other side. The air electrode (cathode) is formed. These fuel electrode and air electrode are both porous bodies formed of conductive ceramics.

  A pipe 556 and a pipe 564 are connected to the cell stack 510. The pipe 556 is a pipe for supplying a hydrogen-containing gas (hereinafter also referred to as “fuel gas”) generated in the reformer 520 described later to the cell stack 510. The fuel gas supplied to the cell stack 510 through the pipe 556 reaches the fuel electrode of each single cell and is used for power generation.

  The pipe 564 is a pipe for supplying power generation air (oxidant) fed from an air blower 562 described later to the cell stack 510. The air supplied to the cell stack 510 through the pipe 564 reaches the air electrode of each single cell and is used for power generation.

  The combustor 530 is a burner for burning the remaining fuel gas discharged from the cell stack 510 without contributing to power generation. A pipe 557, a pipe 565, and a pipe 591 are connected to the combustor 530, respectively.

  The pipe 557 is a pipe for supplying the remaining fuel gas discharged from the cell stack 510 to the combustor 530. One end of the pipe 557 is connected to the cell stack 510, and the other end is connected to the combustor 530.

  The pipe 565 is a pipe for supplying the remaining air discharged from the cell stack 510 without contributing to power generation to the combustor 530. One end of the pipe 565 is connected to the cell stack 510, and the other end is connected to the combustor 530.

  In the combustor 530, the mixed gas of the residual fuel gas that has passed through the pipe 557 and the residual air that has passed through the pipe 565 is burned, and high-temperature combustion exhaust gas is generated. The pipe 591 is a pipe for discharging the combustion exhaust gas generated in this way to the outside. One end of the pipe 591 is connected to the combustor 530. Further, the other end of the pipe 591 is branched into two pipes (a pipe 592 and a pipe 595).

  The pipe 592 is a pipe that connects the downstream end of the pipe 591 and a heat exchanger 580 described later. The combustion exhaust gas supplied to the heat exchanger 580 through the pipe 592 is subjected to heat exchange in the heat exchanger 580 and then discharged to the outside through the pipe 594.

  The pipe 595 is a pipe that connects the downstream end of the pipe 591 and a heat exchanger 570 described later. The combustion exhaust gas supplied to the heat exchanger 570 through the pipe 595 is subjected to heat exchange in the heat exchanger 570 and then discharged to the outside through the pipe 596.

  The reformer 520 receives the supply of raw fuel gas (city gas) and steam and performs steam reforming, thereby generating fuel gas. An upstream end of a pipe 556 is connected to the reformer 520. The reformer 520 is also connected to the downstream end of the pipe 555. The pipe 555 is a pipe for supplying raw fuel gas, steam, and the like to the reformer 520. The upstream end of the pipe 555 is connected to the discharge port 131 of the ejector 10.

  The reformer 520 is filled with a large number of reforming catalysts (not shown) formed by supporting a catalytic metal such as nickel on the surface of an alumina sphere. When the raw fuel gas and water vapor that have passed through the pipe 555 are supplied to the reformer 520, they come into contact with the reforming catalyst to cause a steam reforming reaction, thereby generating fuel gas. As described above, the fuel gas is supplied to the cell stack 510 through the pipe 556.

  In order for the steam reforming reaction to occur in the reformer 520, the reformer 520 and the internal reforming catalyst need to be at a high temperature (about 700 ° C.). In addition, since the steam reforming reaction is an endothermic reaction, heat must be continuously applied to the reformer 520 from the outside in order to maintain the reaction. In the present embodiment, a part of the pipe 592 through which the combustion exhaust gas passes is disposed in the vicinity of the reformer 520. Specifically, a part of the pipe 592 is in contact with the outer wall surface of the reformer 520, and the heat of the combustion exhaust gas passing through the pipe 592 is transmitted to the reformer 520. The steam reforming reaction inside the reformer 520 is maintained by the heat of the combustion exhaust gas.

  The flow of air supplied to the cell stack 510 will be described. Air is supplied from the air supply source 560 through the pipe 561 to the fuel cell system 500 and is sent to the cell stack 510 by the air blower 562. The pipe 561 is a pipe that connects the air supply source 560 and the air blower 562. In the present embodiment, the air supply source 560 is the atmosphere.

  A heat exchanger 580 is provided between the air blower 562 and the cell stack 510. The air blower 562 and the heat exchanger 580 are connected by a pipe 563, and the heat exchanger 580 and the cell stack 510 are connected by a pipe 564. The heat exchanger 580 is a heat exchanger for heating air by performing heat exchange between the high-temperature combustion exhaust gas passing through the pipe 592 and the air passing through the pipe 563. The air is heated in the heat exchanger 580 to increase its temperature, and then supplied to the cell stack 510 through the pipe 564.

  The flow of steam supplied to the reformer 520 will be described. Liquid water, which is a raw material of water vapor, is supplied from the water supply source 550 through the pipe 551 to the fuel cell system 500 and is sent to the reformer 520 side by the water supply pump 552. However, the water supply pump 552 and the reformer 520 are not directly connected, and the heat exchanger 570 and the ejector 10 are disposed between the two. In this embodiment, the water supply source 550 is a water supply tank.

  The water supply pump 552 and the heat exchanger 570 are connected by a pipe 553, and the heat exchanger 570 and the ejector 10 are connected by a pipe 554. The downstream end of the pipe 554 is connected to the supply port 310 in the ejector 10.

  The heat exchanger 570 is a heat exchanger for generating water vapor by heating the water by causing heat exchange between the high-temperature combustion exhaust gas passing through the pipe 595 and the water passing through the pipe 553. Water is heated in the heat exchanger 570 to become water vapor, and then supplied to the supply port 310 of the ejector 10 through the pipe 554. Thereby, water vapor is injected from the injection port 320 of the nozzle 300 inside the ejector 10. That is, in the present embodiment, the water vapor generated in the heat exchanger 570 is ejected from the nozzle 300 as a driving fluid.

  The flow of the raw fuel gas supplied to the reformer 520 will be described. City gas, which is raw fuel gas, is supplied from the raw fuel supply source 540 to the fuel cell system 500 through the pipe 541 and sent to the reformer 520 side by the gas blower 542. However, the gas blower 542 and the reformer 520 are not directly connected, and the ejector 10 is disposed between the two. In this embodiment, the raw fuel supply source 540 is a gas meter.

  The gas blower 542 and the ejector 10 are connected by a pipe 543. The downstream end of the pipe 543 is connected to the first suction unit 210 in the ejector 10. In the present embodiment, the raw fuel gas sent from the gas blower 542 is sucked as a driven fluid in the first suction unit 210. The pipe 543 corresponds to a “first flow path” through which the driven fluid flows. The raw fuel gas sucked in the first suction unit 210 is mixed with water vapor or the like inside the ejector 10 and supplied to the reformer 520 through the pipe 555.

  A pipe 557 connecting the cell stack 510 and the combustor 530 is branched in the middle, and the downstream end of the branched pipe 558 is connected to the second suction part 220 of the ejector 10. In the present embodiment, a part of the remaining fuel gas flowing through the pipe 557 flows through the pipe 558 toward the ejector 10 and is then sucked as a driven fluid in the second suction unit 220. The pipe 558 corresponds to a “second flow path” through which the driven fluid flows. The remaining fuel gas sucked in the second suction unit 220 is mixed with water vapor and raw fuel gas inside the ejector 10 and supplied to the reformer 520 through the pipe 555. With such a configuration, steam and hydrogen contained in the remaining fuel gas are reused for steam reforming and power generation.

  In this embodiment, liquid water is pressurized by the water supply pump 552 and then becomes water vapor and used as a driving fluid. For this reason, the energy required for pressurization is very small as compared with an embodiment in which gas is pressurized by a pump and the gas is used as a driving fluid. Since the energy required for the operation of the water supply pump 552 is small, the operation efficiency of the fuel cell system 500 is high.

  In the present embodiment, the operation of the gas blower 542 is controlled so that the pressure of the raw fuel gas inside the pipe 543 is higher than the pressure of the remaining fuel gas inside the pipe 558. If the pressure of the raw fuel gas inside the pipe 543 is lower than the pressure of the remaining fuel gas inside the pipe 558, the pipe 543 is connected to the second suction part 220, and the pipe 558 is It is desirable to be connected to one suction part 210.

  Note that, in place of the ejector 10, any of the ejectors 10 </ b> A, 10 </ b> B, and 10 </ b> C may be used in the fuel cell system 500.

  In addition to the refrigeration cycle 400 and the fuel cell system 500, the ejector 10 and the like can be used in various types of fluid circulation systems.

  The embodiments of the present invention have been described above with reference to specific examples. However, the present invention is not limited to these specific examples. In other words, those specific examples that have been appropriately modified by those skilled in the art are also included in the scope of the present invention as long as they have the characteristics of the present invention. For example, the elements included in each of the specific examples described above and their arrangement, materials, conditions, shapes, sizes, and the like are not limited to those illustrated, and can be changed as appropriate. Moreover, each element with which each embodiment mentioned above is provided can be combined as long as technically possible, and the combination of these is also included in the scope of the present invention as long as it includes the features of the present invention.

10, 10A, 10B, 10C, 10D: Ejector 100: Case 210: First suction unit 211: First suction port 220: Second suction unit 221: Second suction port 300: Nozzle 320: Ejection port 400, 400D: Freezing Cycle 500: Fuel cell system 520: Reformer

Claims (12)

An ejector (10, 10A, 10B, 10C) for sucking a driven fluid using a flow of the driving fluid,
A case (100) in which a space is formed;
Inside the case, a nozzle (300) for injecting driving fluid from an injection port (320)
A first suction part (210) and a second suction part (220) for guiding the driven fluid to be sucked into the case;
A first suction port (211) that is an outlet of the driven fluid is formed at the downstream end of the first suction unit,
A second suction port (221) that is an outlet of the driven fluid is formed at the downstream end of the second suction unit,
Inside the case, the first suction port and the second suction port are formed at positions where the coordinates in the direction in which the driving fluid flows are different from each other. When the driving fluid is ejected from the nozzle,
2. The ejector according to claim 1, wherein the pressure at the position of the second suction port is lower than the pressure at the position of the first suction port inside the case.   In the case, the distance from the ejection port to the second suction port in the direction in which the driving fluid flows is shorter than the distance from the ejection port to the first suction port in the direction in which the driving fluid flows. The ejector according to claim 2.   The ejector according to claim 2, wherein both the first suction port and the second suction port are formed at a position upstream of the ejection port in a direction in which the driving fluid flows. One of the first suction port and the second suction port is formed at a position upstream of the ejection port in the direction in which the driving fluid flows,
The ejector according to claim 2, wherein the other of the first suction port and the second suction port is formed at a position downstream of the ejection port in the direction in which the driving fluid flows.   The ejector according to claim 2, wherein both the first suction port and the second suction port are formed at a position downstream of the ejection port in the direction in which the driving fluid flows.   At least one of the first direction in which the driven fluid flows through the first suction unit and the second direction in which the driven fluid flows through the second suction unit is ejected from the nozzle. The ejector according to claim 2, wherein the ejector is in the same direction as the direction to be measured. A fluid circulation system (400, 500) using an ejector that sucks a driven fluid using a flow of a driving fluid,
The ejector is
A case where a space is formed inside,
Inside the case, a nozzle that ejects driving fluid from an ejection port;
A first suction part and a second suction part for guiding the driven fluid to be sucked into the case;
A first suction port that is an outlet of the driven fluid is formed at the downstream end of the first suction unit,
A second suction port that is an outlet of the driven fluid is formed at the downstream end of the second suction unit,
In the inside of the case, the first suction port and the second suction port are formed at positions where coordinates in a direction in which the driving fluid flows are different from each other. When the driving fluid is ejected from the nozzle,
The fluid circulation system according to claim 8, wherein the pressure at the position of the second suction port is lower than the pressure at the position of the first suction port inside the case. A first channel (406, 408, 543) that is a channel through which the driven fluid flows;
A flow path through which the driven fluid flows, and a second flow path (407, 409, 558) in which the internal pressure is lower than the internal pressure of the first flow path,
The fluid circulation system according to claim 8, wherein the first flow path is connected to the first suction section, and the second flow path is connected to the second suction section. A condenser (420) for condensing the refrigerant;
A refrigeration cycle (400) comprising a first evaporator (431) and a second evaporator (432) for evaporating the refrigerant,
The refrigerant pressure inside the second evaporator is lower than the refrigerant pressure inside the first evaporator,
From the nozzle, the refrigerant discharged from the condenser is jetted as a driving fluid,
In the first suction part, the refrigerant discharged from the first evaporator is sucked as a driven fluid,
The fluid circulation system according to claim 8, wherein in the second suction unit, the refrigerant discharged from the second evaporator is sucked as a driven fluid. A reformer (520) that receives the supply of raw fuel gas and steam to perform steam reforming, thereby generating fuel gas;
A fuel cell system (500) including a cell stack (510) that generates power upon receiving fuel gas supply,
Water vapor is jetted from the nozzle as a driving fluid,
In one of the first suction part and the second suction part, raw fuel gas is sucked as a driven fluid,
The fluid according to claim 8, wherein the remaining fuel gas discharged from the cell stack without contributing to power generation is sucked as a driven fluid in the other of the first suction portion and the second suction portion. Circulation system.

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