US20190032679A1 - Ejector, ejector production method, and method for setting outlet flow path of diffuser - Google Patents

Ejector, ejector production method, and method for setting outlet flow path of diffuser Download PDF

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Publication number
US20190032679A1
US20190032679A1 US16/147,040 US201816147040A US2019032679A1 US 20190032679 A1 US20190032679 A1 US 20190032679A1 US 201816147040 A US201816147040 A US 201816147040A US 2019032679 A1 US2019032679 A1 US 2019032679A1
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United States
Prior art keywords
flow path
ejector
tapered
tapered surface
diffuser
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Abandoned
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US16/147,040
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English (en)
Inventor
Fumihiro KAWASHIMA
Tomonori ITOGA
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TLV Co Ltd
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TLV Co Ltd
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Assigned to TLV CO., LTD. reassignment TLV CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAWASHIMA, FUMIHIRO, ITOGA, TOMONORI
Publication of US20190032679A1 publication Critical patent/US20190032679A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F04F5/16—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/14—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid
    • F04F5/16—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids
    • F04F5/18—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow the inducing fluid being elastic fluid displacing elastic fluids for compressing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F04F5/461—Adjustable nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F04F5/469—Arrangements of nozzles for steam engines

Definitions

  • the technique disclosed herein relates to an ejector configured to suck second fluid by negative pressure generated by ejection of first fluid to discharge the second fluid together with the first fluid, the method for manufacturing the ejector, and the method for setting an outlet flow path of a diffuser used for the ejector.
  • a general ejector is disclosed in Japanese Patent Publication No. 2000-356305.
  • negative pressure pressure drop
  • second fluid drive target fluid
  • the first fluid and the second fluid are mixed and discharged from a diffuser (an outlet).
  • An expanded flow path (a flow path whose flow path sectional area increases toward a downstream side) is provided at the diffuser.
  • a discharge pressure might change due to, e.g., a change in operation conditions (the usage amount or usage pressure of the fluid mixture) of the apparatus as a steam supply destination.
  • the discharge flow rate of the ejector decreases, and the discharge pressure increases.
  • the discharge pressure becomes too high, the second fluid is less sucked, and eventually, the suction flow rate of the second fluid significantly decreases.
  • an ejector configured so that a sufficient suction flow rate of second fluid can be ensured until the highest possible discharge pressure has been demanded.
  • Performance of the ejector such as the discharge pressure of the fluid mixture and the suction flow rate of the second fluid varies according to the specifications, i.e., the dimensions, of the flow path of the diffuser. Note that various dimensions of the flow path of the diffuser influence the performance of the ejector, and for this reason, a change in the dimensions of the diffuser might lower the performance of the ejector.
  • the technique disclosed herein has been made in view of the above-described situation, and an object of the technique is to reduce degradation of the performance of the ejector upon a simultaneous change of an upper discharge pressure limit for ensuring a second fluid suction flow rate.
  • the ejector disclosed herein includes a nozzle configured to eject first fluid, a suction chamber configured to house the nozzle and to suck second fluid by negative pressure generated by ejection of the first fluid from the nozzle, and a diffuser including an outlet flow path and configured to mix and discharge the first fluid and the second fluid of the suction chamber.
  • the outlet flow path includes a narrowed flow path having a first tapered surface narrowed toward downstream, a parallel flow path connected to a downstream end of the narrowed flow path and having a constant sectional area, and an expanded flow path connected to a downstream end of the parallel flow path and having a second tapered surface expanded toward downstream.
  • the diffuser further includes a changing unit configured to change the dimensions of the outlet flow path. The changing unit changes the dimensions of the outlet flow path such that the ratio of the tapered angle of the first tapered surface to the tapered angle of the second tapered surface is higher as the sectional area of the parallel flow path is smaller.
  • the method for manufacturing the ejector as disclosed herein includes the setting step of setting the dimensions of the outlet flow path, and the preparation step of preparing the diffuser having the dimensions of the outlet flow path set at the setting step.
  • the dimensions of the outlet flow path are set such that the ratio of the tapered angle of the first tapered surface to the tapered angle of the second tapered surface is higher as the sectional area of the parallel flow path is smaller.
  • the method for setting the outlet flow path of the diffuser as disclosed herein includes the step of setting the sectional area of the parallel flow path, and the step of setting the dimensions of the outlet flow path such that the ratio of the tapered angle of the first tapered surface to the tapered angle of the second tapered surface is higher as the sectional area of the parallel flow path is smaller.
  • the ejector can be provided, which is configured to reduce degradation of the performance of the ejector upon a simultaneous change of the upper discharge pressure limit for ensuring the suction flow rate of the second fluid.
  • the ejector can be realized, which is configured to reduce degradation of the performance of the ejector upon a simultaneous change of the upper discharge pressure limit for ensuring the suction flow rate of the second fluid.
  • FIG. 1 is a schematic view of a configuration of an ejector according to an embodiment.
  • FIG. 2 is a graph of a relationship between a discharge pressure and a suction flow rate.
  • FIG. 3 is a schematic sectional view of a diffuser to which a first attachment is attached.
  • FIG. 4 is a schematic sectional view of a diffuser to which a second attachment is attached.
  • An ejector 10 is a steam ejector configured to suck low-pressure steam (second fluid) by ejection of high-pressure steam (first fluid), thereby mixing and discharging these types of steam. That is, in the ejector 10 , the high-pressure steam is drive fluid, and the low-pressure steam is suction fluid.
  • the ejector 10 includes a nozzle 20 , a suction chamber 30 , and a diffuser 40 .
  • An inflow pipe 91 connected to a high-pressure steam supply source is connected to the nozzle 20 .
  • the nozzle 20 is configured to eject the supplied high-pressure steam.
  • a tip end portion of the nozzle 20 is housed in the suction chamber 30 .
  • a low-pressure steam suction port 31 is provided at the suction chamber 30 .
  • negative pressure pressure drop
  • the low-pressure steam is sucked into the suction chamber 30 through the suction port 31 . That is, in the suction chamber 30 , suction force for sucking the low-pressure steam is generated by the negative pressure generated by a jet pump effect of the high-pressure steam.
  • a suction pipe 92 connected to a low-pressure steam supply source is connected to the suction port 31 .
  • the diffuser 40 is connected to the suction chamber 30 .
  • the diffuser 40 is configured to mix and discharge the high-pressure steam ejected to the suction chamber 30 and the low-pressure steam sucked into the suction chamber 30 .
  • An outflow pipe 93 connected to a steam mixture supply destination is connected to a downstream end of the diffuser 40 .
  • the diffuser 40 has a divided structure including an upstream portion 41 , an attachment 42 , and a downstream portion 43 .
  • An upstream end of the upstream portion 41 is connected to the suction chamber 30 .
  • a flange 41 a is provided at a downstream end of the upstream portion 41 .
  • a first flange 43 a is provided at an upstream end of the downstream portion 43
  • a second flange 43 b is provided at a downstream end of the downstream portion 43 .
  • the downstream portion 43 is connected to the outflow pipe 93 through the second flange 43 b .
  • the attachment 42 is sandwiched between the upstream portion 41 and the downstream portion 43 .
  • the flange 41 a of the upstream portion 41 and the first flange 43 a of the downstream portion 43 are fastened with bolts 44 , and in this manner, the attachment 42 is held by the upstream portion 41 and the downstream portion 43 . That is, the attachment 42 can be replaced by loosening of the fastened bolts 44 .
  • the attachment 42 is one example of a changing unit.
  • An outlet flow path 50 of the high-pressure steam and the low-pressure steam is formed at the diffuser 40 , the outlet flow path 50 communicating with the suction chamber 30 .
  • the outlet flow path 50 includes a narrowed flow path 51 , a parallel flow path 52 , and an expanded flow path 53 in this order from an upstream side.
  • the section of the outlet flow path 50 is in a substantially circular shape.
  • the diffuser 40 decreases the velocity of the steam mixture and increases the pressure of the steam mixture when the steam mixture flows in the expanded flow path 53 .
  • An upstream end of the narrowed flow path 51 opens to the suction chamber 30 .
  • the upstream end of the narrowed flow path 51 faces a downstream end of the nozzle 20 in the suction chamber 30 .
  • the sectional area, i.e., the inner diameter, of the narrowed flow path 51 gradually decreases toward a downstream side. That is, the narrowed flow path 51 has a first tapered surface 54 narrowed toward the downstream side.
  • the parallel flow path 52 is connected to a downstream end of the narrowed flow path 51 .
  • the parallel flow path 52 is a flow path having a constant sectional area, i.e., a constant inner diameter.
  • the parallel flow path 52 is a portion having the smallest inner diameter in the outlet flow path 50 , and forms a so-called throat portion.
  • the expanded flow path 53 is connected to a downstream end of the parallel flow path 52 .
  • the sectional area, i.e., the inner diameter, of the expanded flow path 53 gradually increases toward the downstream side. That is, the expanded flow path 53 has a second tapered surface 55 expanded toward the downstream side.
  • the narrowed flow path 51 is formed from the upstream portion 41 to the attachment 42 .
  • the parallel flow path 52 is formed at the attachment 42 .
  • the expanded flow path 53 is formed from the attachment 42 to the downstream portion 43 . That is, at least an upstream end portion of the narrowed flow path 51 is formed at the upstream portion 41 .
  • At least a downstream end portion of the narrowed flow path 51 , the parallel flow path 52 , and at least an upstream end portion of the expanded flow path 53 are formed at the attachment 42 .
  • At least a downstream end portion of the expanded flow path 53 is formed at the downstream portion 43 .
  • the high-pressure steam flowing in the inflow pipe 91 is ejected to the suction chamber 30 through the nozzle 20 , and the low-pressure steam is sucked into the suction chamber 30 through the suction port 31 by ejection of the high-pressure steam. Then, the high-pressure steam and the low-pressure steam in the suction chamber 30 are mixed together, and are discharged from the diffuser 40 .
  • the steam discharged from the diffuser 40 is supplied to an apparatus on the downstream side.
  • the flow velocity of the steam mixture reaches about a sound velocity at the parallel flow path 52 of the diffuser 40 . Thereafter, when the steam mixture flows in the expanded flow path 53 , the velocity of the steam mixture is decreased, and the pressure of the steam mixture is increased.
  • the discharge pressure of the ejector 10 might increase according to an operation status or a specification change of the apparatus as the steam supply destination. However, as illustrated in FIG. 2 , there is an upper discharge pressure limit (this discharge pressure will be hereinafter referred to as a “maximum discharge pressure”) for ensuring a low-pressure steam suction flow rate in the ejector 10 .
  • a suction pressure When the discharge pressure increases beyond the maximum discharge pressure Pmax, a suction pressure also starts increasing. Eventually, the flow velocity in the parallel flow path 52 decreases as compared to the sound velocity, and a non-critical state is brought. Accordingly, the suction pressure increases to a value substantially equal to the discharge pressure. That is, when the discharge pressure exceeds the maximum discharge pressure Pmax, the low-pressure steam suction flow rate decreases rapidly.
  • the maximum discharge pressure Pmax can be changed according to the specifications, i.e., the dimensions, of the outlet flow path 50 .
  • the diffuser 40 is configured such that the dimensions of the outlet flow path 50 is changeable by replacement of the attachment 42 .
  • the inner diameter D of the parallel flow path 52 is decreased in order to increase the maximum discharge pressure Pmax.
  • the flow velocity of the steam mixture in the parallel flow path 52 increases, and therefore, a critical state of the pressure in the parallel flow path 52 is easily ensured.
  • the performance of the ejector 10 relates to various dimensions of the outlet flow path 50 , and other dimensions of the parallel flow path 52 than the inner diameter D need to be changed.
  • the dimensions of the outlet flow path 50 are set such that the ratio (hereinafter referred to as a “tapered angle ratio”) ⁇ / ⁇ of the tapered angle ⁇ of the first tapered surface 54 to the tapered angle ⁇ of the second tapered surface 55 is higher as the sectional area, i.e., the inner diameter D, of the parallel flow path 52 is smaller.
  • the inner diameter D of the parallel flow path 52 is set smaller for a higher target maximum discharge pressure.
  • the tapered angles ⁇ , ⁇ are set such that the tapered angle ratio ⁇ / ⁇ is higher as the inner diameter D is smaller.
  • the upstream portion 41 and the downstream portion 43 are not replaceable.
  • the entire length of the attachment 42 , the inner diameter of the narrowed flow path 51 at an upstream end of the attachment 42 , and the inner diameter of the expanded flow path 53 at a downstream end of the attachment 42 are not changed.
  • the tapered angle ⁇ of a portion of the first tapered surface 54 formed at the attachment 42 and the tapered angle ⁇ of a portion of the second tapered surface 55 formed at the attachment 42 are changed.
  • the “tapered angle ⁇ ” and the “tapered angle ⁇ ” will hereinafter mean the tapered angles of the tapered surface portions formed at the attachment 42 .
  • the tapered angle ⁇ of the first tapered surface 54 is changed greater for a smaller inner diameter D.
  • the tapered angles ⁇ , ⁇ are set such that the tapered angle ratio ⁇ / ⁇ is higher as the inner diameter D is smaller. That is, in a case where at least one of the tapered angles ⁇ , ⁇ needs to increase as the inner diameter D gets lower, the tapered angle ⁇ is more increased, and an increase in the tapered angle ⁇ is suppressed.
  • the tapered angles ⁇ , ⁇ are set such that the increase rate of the tapered angle ⁇ (i.e., the tapered angle ⁇ after change/the tapered angle ⁇ before change) is greater than the increase rate of the tapered angle ⁇ (i.e., the tapered angle ⁇ after change/the tapered angle ⁇ before change).
  • the tapered angle ⁇ of the first tapered surface 54 and the tapered angle ⁇ of the second tapered surface 55 might influence turbulence of the flow of the steam mixture. Greater angles result in more flow turbulence due to separation. Greater flow turbulence results in lower performance of the ejector 10 .
  • the tapered angle ⁇ of the expanded flow path 53 more influences flow turbulence as compared to the tapered angle ⁇ of the narrowed flow path 51 .
  • the tapered angles ⁇ , ⁇ need to increase as the inner diameter D of the parallel flow path 52 gets lower, the tapered angle ⁇ is more greatly changed, and an increase in the tapered angle ⁇ is suppressed. In this manner, worsening of flow turbulence can be reduced, and degradation of the performance of the ejector 10 can be reduced.
  • the length P of the parallel flow path 52 is set shorter for a smaller inner diameter D.
  • the length P of the parallel flow path 52 is set to satisfy the following expression (1), i.e., in proportion to the inner diameter D.
  • the length Q of the narrowed flow path 51 is also shorter as the inner diameter D gets smaller.
  • the length of the expanded flow path 53 is set to such a value that the performance of the ejector 10 is not influenced even when the lengths of the narrowed flow path 51 and the parallel flow path 52 are changed.
  • FIG. 3 is a schematic sectional view of the diffuser 40 to which a first attachment 42 A is attached
  • FIG. 4 is a schematic sectional view of the diffuser 40 to which a second attachment 42 B is attached.
  • the first attachment 42 A has the parallel flow path 52 whose inner diameter D is d 1 .
  • the length p 1 of the parallel flow path 52 is M ⁇ d 1 .
  • the length of the narrowed flow path 51 is q 1 .
  • the tapered angle ⁇ 1 of a portion of the first tapered surface 54 formed at the first attachment 42 A is the same as the tapered angle ⁇ 0 of a portion of the first tapered surface 54 formed at the upstream portion 41 .
  • the tapered angle ⁇ 1 of a portion of the second tapered surface 55 formed at the first attachment 42 A is the same as the tapered angle ⁇ 0 of a portion of the second tapered surface 55 formed at the downstream portion 43 .
  • the second attachment 42 B has the parallel flow path 52 whose inner diameter D is d 2 .
  • the length p 2 of the parallel flow path 52 at the second attachment 42 B is M ⁇ d 2 .
  • the length of the narrowed flow path 51 is q 2 .
  • the tapered angle ⁇ 2 of a portion of the first tapered surface 54 formed at the second attachment 42 B is greater than the tapered angle ⁇ 0 of the portion of the first tapered surface 54 formed at the upstream portion 41 .
  • the tapered angle ⁇ 2 of a portion of the second tapered surface 55 formed at the second attachment 42 B is greater than the tapered angle ⁇ 0 of the portion of the second tapered surface 55 formed at the downstream portion 43 .
  • the inner diameter d 2 of the parallel flow path 52 of the second attachment 42 B is smaller than the inner diameter d 1 of the parallel flow path 52 of the first attachment 42 A, and therefore, the parallel flow path 52 of the second attachment 42 B is shorter than the parallel flow path 52 of the first attachment 42 A.
  • the tapered angle ⁇ 2 of the first tapered surface 54 of the second attachment 42 B is greater than the tapered angle ⁇ 1 of the first tapered surface 54 of the first attachment 42 A
  • the tapered angle ⁇ 2 of the second tapered surface 55 of the second attachment 42 B is greater than the tapered angle ⁇ 1 of the second tapered surface 55 of the first attachment 42 A
  • the tapered angle ratio ⁇ 2 / ⁇ 2 of the second attachment 42 B is greater than the tapered angle ratio ⁇ 1 / ⁇ 1 of the first attachment 42 A. That is, when the inner diameter D is changed from d 1 to d 2 , the increase rate of the tapered angle ⁇ is greater than the increase rate of the tapered angle ⁇ .
  • the inner diameter d 2 of the parallel flow path 52 of the second attachment 42 B is smaller than that of the first attachment 42 A, and therefore, the maximum discharge pressure Pmax of the diffuser 40 into which the second attachment 42 B is incorporated is higher than that in the case of incorporating the first attachment 42 A.
  • the tapered angle ⁇ is more increased, and an increase in the tapered angle ⁇ is suppressed. In this manner, degradation of the performance of the ejector 10 is reduced. Specifically, the tapered angle ⁇ of the first tapered surface 54 and the tapered angle ⁇ of the second tapered surface 55 are increased, and therefore, flow turbulence might occur.
  • the tapered angle ⁇ of the first tapered surface 54 is more increased, and an increase in the tapered angle ⁇ of the second tapered surface 55 is suppressed.
  • worsening of flow turbulence can be reduced.
  • the maximum discharge pressure Pmax can be increased with a sufficient suction flow rate being ensured. Note that the inner diameter D of the parallel flow path 52 is decreased, and therefore, the low-pressure steam suction flow rate is slightly decreased.
  • the tapered angle ratio ⁇ 2 / ⁇ 2 at the second attachment 42 B is, with reference to the tapered angle ⁇ 0 at the upstream portion 41 and the tapered angle ⁇ 0 at the downstream portion 43 , greater than the tapered angle ratio ⁇ 0 / ⁇ 0 at the upstream portion 41 and the downstream portion 43 .
  • the tapered angle ⁇ is more increased as compared to the tapered angle ⁇ , and an increase in the tapered angle ⁇ is suppressed.
  • the low-pressure steam suction flow rate can be ensured even when the discharge pressure of the ejector 10 increases due to the operation status or the specification change of the apparatus as the steam supply destination.
  • the method for manufacturing the ejector 10 includes the setting step of setting the dimensions of the outlet flow path 50 , and the preparation step of preparing the diffuser 40 having the dimensions set at the setting step.
  • the inner diameter D and the length P of the parallel flow path 52 , the tapered angle ⁇ of the first tapered surface 54 , and the tapered angle ⁇ of the second tapered surface 55 at the attachment 42 are set.
  • the tapered angles ⁇ , ⁇ are set such that the tapered angle ratio ⁇ / ⁇ is higher as the sectional area, i.e., the inner diameter D, of the parallel flow path 52 is smaller.
  • the inner diameter D i.e., the sectional area
  • the length P of the parallel flow path 52 is set based on the expression (1).
  • the tapered angles ⁇ , ⁇ are set such that the tapered angle ratio ⁇ / ⁇ is higher as the inner diameter D is smaller.
  • a relationship among the inner diameter D and the tapered angles ⁇ , ⁇ is obtained in advance.
  • the corresponding tapered angles ⁇ , ⁇ are set.
  • the diffuser 40 having the dimensions of the outlet flow path 50 set at the setting step is prepared.
  • the attachment 42 having the dimensions of the outlet flow path 50 set at the setting step is produced.
  • the attachment 42 suitable for the operation status or the specifications of the apparatus as the steam supply destination is selected from multiple attachments 42 having different inner diameters D of the narrowed flow path 51 and having a greater tapered angle ratio ⁇ / ⁇ for a smaller inner diameter D.
  • the method for manufacturing the ejector 10 further includes an assembly step.
  • the nozzle 20 , the suction chamber 30 , and the diffuser 40 are assembled together. Specifically, the nozzle 20 and the upstream portion 41 of the diffuser 40 are attached to the suction chamber 30 . Then, the attachment 42 and the downstream portion 43 are attached to the upstream portion 41 with the attachment 42 being sandwiched between the upstream portion 41 and the downstream portion 43 .
  • the attachment 42 having a smaller inner diameter D and a greater tapered angle ratio ⁇ / ⁇ than those before replacement is prepared at the preparation step.
  • Such an attachment 42 is newly produced, or is selected from multiple attachments 42 . Then, the attachment 42 of the ejector 10 is replaced with the attachment 42 prepared at the preparation step.
  • the ejector 10 includes the nozzle 20 configured to eject the high-pressure steam (the first fluid), the suction chamber 30 configured to house the nozzle 20 and to suck the low-pressure steam (the second fluid) by the negative pressure generated by ejection of the high-pressure steam from the nozzle 20 , and the diffuser 40 having the outlet flow path 50 and configured to mix and discharge the high-pressure steam and the low-pressure steam of the suction chamber 30 .
  • the outlet flow path 50 includes the narrowed flow path 51 having the first tapered surface 54 narrowed toward the downstream side, the parallel flow path 52 connected to the downstream end of the narrowed flow path 51 and having the constant sectional area, and the expanded flow path 53 connected to the downstream end of the parallel flow path 52 and having the second tapered surface 55 expanded toward the downstream side.
  • the diffuser 40 further includes the attachment 42 (the changing unit) configured to change the dimensions of the outlet flow path 50 .
  • the attachment 42 changes the dimensions of the outlet flow path 50 such that the ratio ⁇ / ⁇ of the tapered angle ⁇ of the first tapered surface 54 to the tapered angle ⁇ of the second tapered surface 55 is higher as the sectional area of the parallel flow path 52 is smaller.
  • the dimensions of the outlet flow path 50 are changed by the attachment 42 .
  • the maximum discharge pressure Pmax of the ejector 10 can be changed.
  • the dimensions of the outlet flow path 50 are set such that the tapered angle ratio ⁇ / ⁇ is higher as the sectional area of the parallel flow path 52 is smaller. That is, in a case where at least one of the tapered angles ⁇ , ⁇ needs to be increased in response to a decrease in the sectional area of the parallel flow path 52 , the tapered angle ⁇ is more increased, and an increase in the tapered angle ⁇ is suppressed. In this manner, the maximum discharge pressure Pmax of the ejector 10 can be changed.
  • flow disturbance due to an increase in the tapered angles ⁇ , ⁇ can be reduced, and degradation of the performance of the ejector 10 can be reduced.
  • the attachment 42 changes the dimensions of the outlet flow path 50 such that the length P of the parallel flow path 52 is shorter as the sectional area of the parallel flow path 52 is smaller.
  • the attachment 42 changes the dimensions of the outlet flow path 50 such that the length P of the parallel flow path 52 is changed in proportion to the inner diameter D of the parallel flow path 52 .
  • part of the diffuser 40 is formed from the replaceable attachment 42 .
  • the attachment 42 includes at least part of the narrowed flow path 51 , the parallel flow path 52 , and at least part of the expanded flow path 53 .
  • the dimensions of the outlet flow path 50 are changed by replacement of the attachment 42 .
  • the diffuser 40 is configured such that the attachment 42 is replaceable.
  • the outlet flow paths 50 with different dimensions are formed at multiple attachments 42 .
  • the tapered angle ratio ⁇ / ⁇ at the attachment 42 with a smaller inner diameter D is greater than the tapered angle ratio ⁇ / ⁇ at the attachment 42 with a greater inner diameter D.
  • the maximum discharge pressure Pmax of the ejector 10 can be changed by replacement of the attachment 42 without the need for replacement of the entirety of the diffuser 40 , and degradation of the performance of the ejector 10 can be reduced.
  • it is not necessary to replace the entirety of the ejector 10 and therefore, the dimensions of the outlet flow path 50 can be easily changed.
  • the method for manufacturing the ejector 10 includes the setting step of setting the dimensions of the outlet flow path 50 , and the preparation step of preparing the diffuser 40 having the dimensions of the outlet flow path 50 set at the setting step.
  • the dimensions of the outlet flow path 50 are set such that the ratio ⁇ / ⁇ of the tapered angle ⁇ of the first tapered surface 54 to the tapered angle ⁇ of the second tapered surface 55 is higher as the sectional area of the parallel flow path 52 is smaller.
  • the ejectors 10 with different maximum discharge pressures Pmax can be manufactured.
  • the diffuser 40 having the outlet flow path 50 set at the setting step is prepared by replacement of the attachment 42 of the diffuser 40 including the replaceable attachment 42 .
  • the dimensions of the outlet flow path 50 of the diffuser 40 are changed by replacement of the attachment 42 .
  • the dimensions of the narrowed flow path 51 and the parallel flow path 52 can be changed without the need for changing the entirety of the diffuser 40 .
  • the method for setting the outlet flow path of the diffuser 40 includes the step of setting the sectional area of the parallel flow path 52 , and the step of setting the dimensions of the outlet flow path 50 such that the ratio ⁇ / ⁇ of the tapered angle ⁇ of the first tapered surface 54 to the tapered angle ⁇ of the second tapered surface 55 is higher as the sectional area of the parallel flow path 52 is smaller.
  • the embodiment has been described as an example of the technique disclosed in the present application.
  • the technique of the present disclosure is not limited to above, and is also applicable to embodiments to which changes, replacements, additions, omissions, etc. are made as necessary.
  • each component described above in the embodiment may be combined to form a new embodiment.
  • the components described in the detailed description with reference to the attached drawings may include not only components essential for solving the problems, but also components not essential for solving the problems and provided for illustrating the above-described technique by an example.
  • description of the non-essential components in the detailed description with reference to the attached drawings should not be directly recognized as these non-essential components being essential.
  • the above-described embodiment may have the following configurations.
  • the diffuser 40 has the structure divided into three portions, but may have a structure divided into two portions or four or more portions.
  • the method for fixing the attachment 42 is not limited to sandwiching between the upstream portion 41 and the attachment 42 .
  • an optional fixing method can be employed.
  • the diffuser may include a deformable mechanism capable of changing the inner diameter.
  • the deformable mechanism may have a tubular wall portion configured to form the outlet flow path 50 and exhibiting flexibility, and multiple pressing members (e.g., bolts) arranged at the outer periphery of the wall portion in a circumferential direction and configured to press the wall portion inward in a radial direction.
  • the wall portion is deformed in such a manner that the wall portion is pressed inward in the radial direction by the pressing member. Accordingly, the inner diameter of the wall portion is decreased.
  • the inner diameter D i.e., the sectional area
  • multiple sets of the pressing members are provided at different positions of the wall portion in an axial direction thereof, multiple pressing members arranged in the circumferential direction of the wall portion being taken as a single set. That is, depending on at which positions in the axial direction the pressing members are pressed, the length Q of the narrowed flow path 51 can be changed.
  • the tapered angle ⁇ of the first tapered surface 54 , the length Y of the parallel flow path 52 , and the length of the expanded flow path 53 can be changed.
  • tapered angle ⁇ of the second tapered surface 55 can be changed.
  • an optional configuration capable of changing the dimensions of the outlet flow path 50 can be employed.
  • the diffuser 40 has the divided structure including the attachment 42 , but is not limited to above.
  • the diffuser 40 may have an integrated structure.
  • multiple diffusers 40 each have the outlet flow paths 50 with different dimensions, and each diffuser 40 is configured such that the tapered angle ratio ⁇ / ⁇ is higher as the inner diameter D is smaller.
  • the suitable diffuser 40 is selected, and is incorporated into the ejector 10 . That is, at the preparation step in the method for manufacturing the ejector 10 , the diffuser 40 having the dimensions (the inner diameter D and the tapered angles ⁇ , ⁇ ) of the outlet flow path 50 set at the setting step is selected from multiple diffusers 40 , or is newly produced.
  • both of the tapered angle ⁇ of the first tapered surface 54 and the tapered angle ⁇ of the second tapered surface 55 are increased in such a manner that the inner diameter D is decreased from d 1 to d 2 , but the present invention is not limited to these examples. While the tapered angle ⁇ increases as the inner diameter D gets smaller, the tapered angle ⁇ may be held constant or may decrease. Even in this case, an increase in the tapered angle ⁇ is suppressed, and worsening of the flow is reduced.
  • the technique disclosed herein is useful for the ejector, the method for manufacturing the ejector, and the method for setting the outlet flow path of the diffuser used for the ejector.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Nozzles (AREA)
US16/147,040 2016-04-01 2018-09-28 Ejector, ejector production method, and method for setting outlet flow path of diffuser Abandoned US20190032679A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2016-074570 2016-04-01
JP2016074570 2016-04-01
PCT/JP2017/005469 WO2017169219A1 (ja) 2016-04-01 2017-02-15 エゼクタ、エゼクタの製造方法及びディフューザの出口流路の設定方法

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/005469 Continuation WO2017169219A1 (ja) 2016-04-01 2017-02-15 エゼクタ、エゼクタの製造方法及びディフューザの出口流路の設定方法

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US20190032679A1 true US20190032679A1 (en) 2019-01-31

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US (1) US20190032679A1 (ja)
EP (1) EP3438466B1 (ja)
JP (1) JP6352543B2 (ja)
CN (1) CN108884839B (ja)
WO (1) WO2017169219A1 (ja)

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US11156234B2 (en) * 2018-08-24 2021-10-26 Audi Ag Ejector for a fuel cell system and fuel cell system

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Publication number Publication date
WO2017169219A1 (ja) 2017-10-05
EP3438466B1 (en) 2020-04-01
CN108884839A (zh) 2018-11-23
EP3438466A4 (en) 2019-03-27
EP3438466A1 (en) 2019-02-06
CN108884839B (zh) 2020-03-31
JPWO2017169219A1 (ja) 2018-04-05
JP6352543B2 (ja) 2018-07-04

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