US20150152885A1 - Ejector - Google Patents

Ejector Download PDF

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Publication number
US20150152885A1
US20150152885A1 US14/407,452 US201314407452A US2015152885A1 US 20150152885 A1 US20150152885 A1 US 20150152885A1 US 201314407452 A US201314407452 A US 201314407452A US 2015152885 A1 US2015152885 A1 US 2015152885A1
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US
United States
Prior art keywords
ejector
fluid
pressure
fluid nozzle
nozzle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/407,452
Other languages
English (en)
Inventor
Michael Dennis
Original Assignee
Endless Solar Corporation Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AU2012902457A external-priority patent/AU2012902457A0/en
Application filed by Endless Solar Corporation Ltd filed Critical Endless Solar Corporation Ltd
Publication of US20150152885A1 publication Critical patent/US20150152885A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04F5/14—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
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F04F5/463—Arrangements of nozzles with provisions for mixing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/06—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure
    • F25B1/08—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure using vapour under pressure

Definitions

  • the present invention relates to an ejector, such as an ejector for a solar cooling system.
  • Photovoltaic solar panels may be used to convert sunlight into electrical energy that can be used to operate an electric motor that drives a gas compressor of a cooling system. This may reduce the need for fossil fuels, but the efficiency is relatively low and the capital cost is relatively high.
  • Cooling systems that are operated using thermal solar energy and have ejectors instead of corresponding conventional electrical components are an alternative.
  • an ejector is designed for predetermined operation conditions (such as temperatures and pressures of fluids) at which the ejector operates most efficiently. Consequently, the ejector efficiency is reduced if the ejector is not operated at the predetermined operation conditions.
  • the present invention provides in a first aspect an ejector comprising:
  • a fluid nozzle positioned in the housing portion and coupled to the first fluid inlet, the fluid nozzle being arranged such that a first fluid that has a fluid inlet pressure P 1 and is received by the first fluid inlet has a fluid nozzle exit pressure after passing through the fluid nozzle, the fluid nozzle exit pressure being lower than P 1 ;
  • a mixing region arranged such that the first fluid when passing through the mixing region draws a second fluid from the second fluid inlet such that the first and second fluids mix;
  • the ejector is arranged such that a position of an outlet of the fluid nozzle relative to the mixing region is adjusted dependent on P 1 and/or a pressure of the mixed first and second fluids.
  • the ejector may be arranged such that a position of the outlet of the fluid nozzle relative to the mixing region is self-adjusted dependent on P 1 and/or a pressure of the mixed first and second fluids.
  • the ejector may comprise a passive structure that is arranged for self-adjusting of the position of the outlet of the fluid nozzle.
  • the ejector may also comprise an actuator that is arranged to adjust a position of the outlet of the fluid nozzle dependent on P 1 and/or a pressure of the mixed first and second fluids.
  • the ejector is arranged such that the first fluid has a second pressure P 2 after passing through the fluid nozzle, P 2 being lower than P 1 , and the mixture of the first and second fluid exits the ejector with a third pressure P 3 ;
  • the ejector is arranged such that the position of the outlet of the fluid nozzle relative to the mixing region is adjusted dependent on P 1 , P 2 and/or P 3 .
  • the ejector typically comprises an ejector diffuser having an interior portion with a cross-sectional area that increases in diameter in a direction towards the fluid outlet and is arranged such that the mixture of the first and second fluid exits the ejector through the fluid outlet with the third pressure P 3 .
  • the ejector may comprise a converging region that is provided in addition to the mixing region and that is positioned such that the mixed first and second fluids converge before exiting the ejector, the converging region having a cross-sectional area that reduces in diameter in a direction towards the outlet of the ejector.
  • the mixing region may be provided in the form of a converging region and may be arranged such that the first and second fluids converge during or after mixing and before exiting the ejector, the converging region having a cross-sectional area that reduces in diameter in a direction towards the outlet of the ejector.
  • the ejector is typically arranged such that the outlet of the fluid nozzle, and typically the entire fluid nozzle, moves towards or away from the converging region if the pressure of the mixed first and second fluids (such as P 2 or P 3 ) changes relative to another pressure within the ejector.
  • the ejector is typically arranged such that the outlet of the fluid nozzle, and typically the entire fluid nozzle, moves away from the converging region if P 2 increases and towards or into the converging region of P 3 increases.
  • Embodiments of the present invention have significant practical advantages.
  • An ideal position of the fluid nozzle is dependent on P 1 , P 2 and/or P 3 . Consequently, the adjusting of the relative position of the fluid nozzle may increase the ejector's efficiency.
  • a length by which the relative position of the ejector is adjusted is largely proportional to a change in pressure of the mixed first and second fluids (such as P 2 or P 3 ) relative to another pressure in the ejector.
  • the ejector may comprise a conduit that is arranged such that a portion at or near the fluid nozzle of the ejector has a pressure that is proportional to, or substantially equals, a pressure of the mixed first and second fluids and wherein the ejector is arranged such that that portion is isolated form unmixed first and second fluids.
  • the ejector comprises a conduit that is arranged such that a portion at or near the fluid nozzle of the ejector has a pressure that is proportional to, or substantially equals, the pressure P 2 or P 3 and wherein the ejector is arranged such that that portion is isolated form unmixed first and second fluids.
  • the ejector may comprise a diaphragm.
  • the diaphragm may seal at least a portion around the fluid nozzle.
  • the ejector may be arranged such that the fluid nozzle or a portion thereof moves until the diaphragm and/or another portion of the ejector provides a sufficient reaction force for locating the fluid nozzle in an adjusted position.
  • the diaphragm may surround the fluid nozzle or may alternatively only be positioned around a portion of the fluid nozzle.
  • the diaphragm typically comprises a suitable polymeric material, such as a rubber material.
  • the ejector may comprise a moveable wall portion, such as a moveable wall portion that is rigid and may be coupled to a spring.
  • the moveable wall portion may be coupled directly or indirectly to the fluid nozzle such that the fluid nozzle or a portion thereof moves with the moveable wall portion until the spring provides a sufficient reaction force for locating the fluid nozzle in an adjusted position.
  • the conduit may be arranged such that a side portion of the diaphragm or the moveable wall portion is exposed to a pressure that is proportional to, or approximately equals, the pressure of the mixed first and second fluids, wherein the ejector may be arranged such that an increase in the pressure of the mixed first and second fluids relative to another pressure within the ejector results in a movement of the nozzle or portion thereof relative to the mixing region of the ejector.
  • the ejector typically is arranged such that an increase in the pressure of the mixed first and second fluids relative to P 3 results in a movement of the nozzle or portion thereof away from the mixing region of the ejector. Further, the ejector typically is arranged such that an decrease in the pressure of the mixed first and second fluids relative to P 3 results in a movement of the nozzle or portion thereof into or towards the mixing region of the ejector.
  • the present invention also provides a method of operating an ejector, the method comprising:
  • the step of adjusting a position of an outlet of the fluid nozzle relative to the mixing region of the ejector may comprise self-adjusting a position of an outlet of the fluid nozzle.
  • the mixing region may comprise, or may be provided in the form of, the converging region.
  • FIG. 1 shows a schematic cross-sectional representation of an ejector in accordance with an embodiment of the present invention
  • FIGS. 2 and 3 show perspective side views of the ejector in accordance with an embodiment of the present invention
  • FIG. 4 is a flow chart illustrating a method of operating an ejector in accordance with an embodiment of the present invention.
  • FIG. 5 illustrates the operation of a heat pump including the ejector in accordance with a specific embodiment of the present invention.
  • the ejector 100 may be operated to drive a heat pump of a refrigeration cycle, in which case the ejector 100 may be used in place of a conventional electric compressor, which will be described in more details further below with reference to FIG. 5 .
  • the ejector 100 has a body 102 that is generally cylindrical.
  • the body 102 comprises a nozzle housing 104 and a diffuser portion 106 .
  • a fluid nozzle 108 is positioned in the nozzle housing 104 .
  • the body 102 also comprises a mixing region that is provided in the form of a converging region 110 and has a cross-sectional area that reduces in a direction away from the nozzle 108 and along an axis of the ejector 100 .
  • the diffuser portion 106 further comprises a diverging region 118 that has a cross-sectional area that increases in a direction away from the nozzle 108 and along an axis of the ejector 100 .
  • the ejector 100 has a first inlet 114 for receiving a first fluid such as a refrigerant. Further, the ejector 100 has a second inlet 116 for receiving a second fluid that may also be a refrigerant. However, a person skilled in the art will appreciate that the first and second fluids may be of various different types. For example, the first and/or the second fluids may alternatively be air, water, water vapour or refrigerant vapour or any other suitable fluid.
  • the first fluid 114 has a pressure P 1 before penetrating through the nozzle 108 .
  • the nozzle 108 has a diverging region 109 through which the first fluid exits the nozzle 108 and that results in an expansion of the first fluid, which further expands a converging region 110 in which it has a reduced pressure P 2 (and the velocity of the first fluid is increased).
  • the pressure P 2 is sufficiently low such that the second fluid is drawn through the second inlet 116 into the mixing region of the converging region 110 to mix with the first fluid.
  • the mixture of the first and second fluids penetrates through the converging region 110 , a cylindrical region 112 , the diffusing region 118 and then exits the ejector 100 with a pressure P 3 . Consequently, the ejector 100 functions as a pump or compressor that increases the pressure of the second fluid.
  • the efficiency with which the ejector 100 pumps the second fluid depends on various operation parameters including the differences between the pressures P 1 , P 2 and P 3 for a given design of the ejector 100 .
  • the nozzle 108 should be positioned further within the converging region 110 than for smaller P 3 .
  • the nozzle 108 is movable along an axis of the ejector 100 such that positioning of the nozzle 108 as a function of P 3 , P 2 and P 1 is possible.
  • the nozzle 108 has in this embodiment a holder 121 in which the nozzle 108 slides along the axis of the ejector 100 .
  • the ejector 100 also comprises a diaphragm 119 that surrounds the nozzle 108 and seals the nozzle 108 . Further, the ejector 100 comprises a conduit 122 that connects an end-portion of the diffuser region 118 with a volume 123 behind the diaphragm 119 .
  • the volume 123 has a pressure that is in this embodiment proportional to or is substantially equal to the pressure P 3 such that the pressure within the volume 123 pushes on the diaphragm 119 and on the nozzle 108 to move the nozzle 108 to a position at which the diaphragm 119 is sufficiently expanded such that the diaphragm 119 provides a sufficient reaction force and the nozzle is located in an adjustment position.
  • the diaphragm 119 is proportioned and arranged such that the adjustment position enables substantially ideal or at least improved operating condition dependent on P 3 relative to other pressures of the ejector.
  • the nozzle holder 121 is provided with facility for damping the motion of the nozzle 108 such that the nozzle 108 does not change position with rapid fluctuations in pressures P 1 , P 2 or P 3 . Rapid fluctuations in pressure may arise from pressure waves or shock waves in the ejector. Damping may be provided by friction within the nozzle holder 121 . This friction could be provided by including a flexible ring 130 inside the nozzle holder 121 .
  • the ejector 100 may alternatively be provided in different forms.
  • the diaphragm 119 may only partially surround the nozzle 108 and a remaining portion may be solid. Further, the diaphragm 119 may be positioned at another position than indicated in FIG. 1 .
  • the diaphragm 119 may be located further within the ejector 100 and along the nozzle 108 . Further, the diaphragm 119 may be replaced with a suitable spring mechanism (including for example a compression or expansion spring) that is arranged to provide the reaction force for locating the nozzle in an adjustment position.
  • a suitable spring mechanism including for example a compression or expansion spring
  • the ejector 100 may or may not comprise the diaphragm 119 and the pressure P 3 may push against a rigid wall (not shown) that is attached to the movable nozzle 108 to move the nozzle 108 until the spring mechanism provides a sufficient reaction force.
  • the holder 116 may be provided in any suitable form or may not be present.
  • the diaphragm 119 or the rigid wall may be arranged hold the nozzle 108 .
  • an end of the conduit 122 may be positioned near the outlet of the nozzle 108 in the converging region 110 or in the cylindrical region 112 .
  • the ejector 100 may not necessarily comprise a converging region.
  • the mixing region may be incorporated in the diffusing region 118 .
  • the ejector may comprise an actuator that is arranged to adjust the position of the fluid nozzle 108 as a function of P 1 , P 2 or P 3 .
  • the ejector may comprise a pressure sensor that senses a change in P 1 , P 2 or P 3 and generates an output signal that is used to control the actuator.
  • the diaphragm 119 is formed from a suitable polymeric material that has a suitable flexibility, such as a suitable rubber or a thin metallic material.
  • first and second fluids may for example be refrigerants, examples of which include hydrofluorocarbons, hydrocarbons, carbon dioxide, ammonia, alcohols and water.
  • FIG. 4 illustrates a method of operating an ejector in accordance with an embodiment of the present invention.
  • Method 400 comprises steps 402 and 404 of receiving first and second fluids.
  • the method 400 also includes directing the first fluid through a nozzle of an ejector such that the pressure of the first fluid is reduced to a second pressure that is lower than the first pressure.
  • the method 400 further includes drawing the second fluid such that the second fluid mixes with the first fluid that exited an outlet of the nozzle (step 408 ) adjusting a position of the outlet of the nozzle relative to a mixing region of the ejector dependent on the first pressure and/or the a pressure of the mixed first and second fluids to improve the efficiency of the ejector (step 410 ).
  • Step 408 may comprise self-adjusting the position of the outlet of the fluid nozzle.
  • FIG. 5 the operation of the ejector 100 in a heat pump refrigeration cycle is described in more detail.
  • the heat pump refrigeration cycle 500 comprises in this example high and low temperature sub cycles ( 510 and 512 respectively).
  • the high temperature sub cycle 510 heat that is transferred to the ejector 100 from the heat source (such as a solar collector 504 ) through a vapour generator 514 causing vaporisation of the ejector cycle working fluid in the generator 514 at a temperature slightly above the saturation temperature of the refrigerant. Vapour then flows to the ejector 100 where it is accelerated (and reduced in pressure) by the nozzle of the ejector 100 .
  • a pump 516 may be required to generate a pressure difference for the ejector 100 to operate, but since liquid is being compressed, the power consumption is relatively small.
  • the fluids form generator 514 and evaporator 518 then mix in the ejector 100 and the resultant fluid mixture undergoes a compression shock.
  • thermal compression replaces the electrical compressor in a conventional heat pump.
  • Further compression takes place in the diffusing region of the ejector 100 such that a subsonic stream emerging from the ejector 100 then flows into the condenser 520 .
  • the ejector 100 provides for increased efficiency if operation pressures change.
  • Liquid refrigerant leaving the condenser 520 is then divided into two streams; one enters the evaporator 518 after a pressure reduction through the expansion valve 522 , the other is routed back into the generator 514 after undergoing a pressure increase through the refrigerant pump 516 .
  • the refrigerant fluid is evaporated in the evaporator 518 , absorbing heat from the environment that is being cooled, and then it is entrained back into the ejector 100 completing the cycle.
  • Modelling may be based on thermodynamic compressible flow theory with minor corrections for non-ideal behaviour, or numerically derived using computational fluid dynamics and/or finite element analysis. Modelling may be aided with reference to:
  • the ejector may be used for systems in which the inlet and exit fluids are air, water or any other type of suitable fluid.
  • the inlet and exit fluids are air, water or any other type of suitable fluid.
  • at least one of the inlet fluids may be a gaseous medium and the exit fluid may be a liquid.
  • the at least one of the inlet fluids may be a liquid medium and the exit fluid may be a gaseous medium.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Jet Pumps And Other Pumps (AREA)
US14/407,452 2012-06-12 2013-04-16 Ejector Abandoned US20150152885A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AU2012902457 2012-06-12
AU2012902457A AU2012902457A0 (en) 2012-06-12 An ejector
PCT/AU2013/000393 WO2013185164A1 (en) 2012-06-12 2013-04-16 An ejector

Publications (1)

Publication Number Publication Date
US20150152885A1 true US20150152885A1 (en) 2015-06-04

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ID=49757318

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/407,452 Abandoned US20150152885A1 (en) 2012-06-12 2013-04-16 Ejector

Country Status (8)

Country Link
US (1) US20150152885A1 (ja)
EP (1) EP2859242A4 (ja)
JP (1) JP2015521703A (ja)
CN (1) CN104379941A (ja)
AU (1) AU2013273913A1 (ja)
BR (1) BR112014030967A2 (ja)
IN (1) IN2014MN02493A (ja)
WO (1) WO2013185164A1 (ja)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019207738A1 (de) * 2019-05-27 2020-12-03 Robert Bosch Gmbh Diffusor für eine Strahlpumpe und Strahlpumpe
JP2021076038A (ja) * 2019-11-06 2021-05-20 富士電機株式会社 エジェクタ
US11982406B1 (en) 2021-02-08 2024-05-14 United Launch Alliance, L.L.C. Method and apparatus for controlling temperature and pressure inside a propellant tank
US12110911B1 (en) 2021-02-08 2024-10-08 United Launch Alliance, L.L.C. Ejector with integrated isolation valve
WO2024209426A1 (en) * 2023-04-07 2024-10-10 Eaton Intelligent Power Limited Ejector for hydrogen recirculation system

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CN104089439A (zh) * 2014-07-01 2014-10-08 浙江大学宁波理工学院 随蒸发温度自动调节面积比的喷射器及喷射式制冷机
CN104075509A (zh) * 2014-07-01 2014-10-01 浙江大学 随发生温度自动调节面积比的喷射器及喷射式制冷机
CN104075508A (zh) * 2014-07-01 2014-10-01 浙江大学宁波理工学院 随冷凝温度自动调节面积比的喷射器及喷射式制冷机
CN104457008B (zh) * 2014-12-16 2016-10-05 山东大学 一种用于废热驱动的冷链物流喷射式制冷系统的喷射器
KR102303676B1 (ko) * 2014-12-30 2021-09-23 삼성전자주식회사 이젝터 및 이를 갖는 냉동장치
CN104804918A (zh) * 2015-05-13 2015-07-29 贵州珍酒酿酒有限公司 用于谷物和酿酒母液的混合装置
CN104804919A (zh) * 2015-05-13 2015-07-29 贵州珍酒酿酒有限公司 啤酒淀粉糖化可调混合装置
CN107893783B (zh) * 2017-11-24 2019-10-18 中国兵器工业第五九研究所 一种流体喷射泵及流体运输管路
CN109869357A (zh) * 2017-12-02 2019-06-11 哈尔滨工大金涛科技股份有限公司 弹性蒸汽喷射器
US10550012B2 (en) * 2018-01-05 2020-02-04 Culligan International Company Softener eductor with embedded check valve
CN109059298B (zh) * 2018-07-05 2020-11-03 中国矿业大学 流体自混匀装置
US20210123607A1 (en) * 2019-10-28 2021-04-29 Carrier Corporation Thermally enhanced heating
US11293375B2 (en) * 2020-02-12 2022-04-05 General Electric Company Variable area ejector
JP7472675B2 (ja) * 2020-06-22 2024-04-23 株式会社デンソー エジェクタ

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US20070186572A1 (en) * 2006-02-16 2007-08-16 Denso Corporation Refrigerant flow-amount controlling device and ejector refrigerant cycle system using the same
US20090155092A1 (en) * 2007-12-12 2009-06-18 Honda Motor Co., Ltd. Fuel cell system

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Publication number Priority date Publication date Assignee Title
US3701264A (en) * 1971-02-08 1972-10-31 Borg Warner Controls for multiple-phase ejector refrigeration systems
US20020106547A1 (en) * 2001-02-02 2002-08-08 Honda Giken Kogyo Kabushiki Kaisha Variable flow-rate ejector and fuel cell system having the same
US20040040340A1 (en) * 2002-08-29 2004-03-04 Masayuki Takeuchi Refrigerant cycle with ejector having throttle changeable nozzle
US20040172966A1 (en) * 2003-03-05 2004-09-09 Yukikatsu Ozaki Ejector with tapered nozzle and tapered needle
US20070186572A1 (en) * 2006-02-16 2007-08-16 Denso Corporation Refrigerant flow-amount controlling device and ejector refrigerant cycle system using the same
US20090155092A1 (en) * 2007-12-12 2009-06-18 Honda Motor Co., Ltd. Fuel cell system

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019207738A1 (de) * 2019-05-27 2020-12-03 Robert Bosch Gmbh Diffusor für eine Strahlpumpe und Strahlpumpe
JP2021076038A (ja) * 2019-11-06 2021-05-20 富士電機株式会社 エジェクタ
JP7490945B2 (ja) 2019-11-06 2024-05-28 富士電機株式会社 エジェクタ
US11982406B1 (en) 2021-02-08 2024-05-14 United Launch Alliance, L.L.C. Method and apparatus for controlling temperature and pressure inside a propellant tank
US12110911B1 (en) 2021-02-08 2024-10-08 United Launch Alliance, L.L.C. Ejector with integrated isolation valve
WO2024209426A1 (en) * 2023-04-07 2024-10-10 Eaton Intelligent Power Limited Ejector for hydrogen recirculation system

Also Published As

Publication number Publication date
EP2859242A4 (en) 2016-04-13
WO2013185164A1 (en) 2013-12-19
AU2013273913A1 (en) 2014-12-18
IN2014MN02493A (ja) 2015-07-17
JP2015521703A (ja) 2015-07-30
EP2859242A1 (en) 2015-04-15
CN104379941A (zh) 2015-02-25
BR112014030967A2 (pt) 2017-06-27

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