EP4179213A1 - Nozzle appliance for a jet pump and jet pump - Google Patents

Nozzle appliance for a jet pump and jet pump

Info

Publication number
EP4179213A1
EP4179213A1 EP21734289.8A EP21734289A EP4179213A1 EP 4179213 A1 EP4179213 A1 EP 4179213A1 EP 21734289 A EP21734289 A EP 21734289A EP 4179213 A1 EP4179213 A1 EP 4179213A1
Authority
EP
European Patent Office
Prior art keywords
nozzle
mixing tube
fluid
driving
suction 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.)
Withdrawn
Application number
EP21734289.8A
Other languages
German (de)
French (fr)
Inventor
Daniel Kintea
David Schneider
Lukasz Gabrys
Michal Sajdak
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Norma Germany GmbH
Original Assignee
Norma Germany GmbH
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
Application filed by Norma Germany GmbH filed Critical Norma Germany GmbH
Publication of EP4179213A1 publication Critical patent/EP4179213A1/en
Withdrawn legal-status Critical Current

Links

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
    • F04F5/463—Arrangements of nozzles with provisions for mixing
    • 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
    • F04F5/14—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
    • F04F5/20—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 evacuating
    • F04F5/22—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 evacuating of multi-stage type
    • 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
    • F04F5/20—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 evacuating
    • 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
    • F04F5/24—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 liquids, e.g. containing solids, or liquids and 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
    • F04F5/24—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 liquids, e.g. containing solids, or liquids and elastic fluids
    • F04F5/26—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 liquids, e.g. containing solids, or liquids and elastic fluids of multi-stage type
    • 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
    • F04F5/467—Arrangements of nozzles with a plurality of nozzles arranged in series

Definitions

  • the present invention relates to a nozzle appliance for a jet pump, comprising a driving nozzle and a first suction nozzle, wherein the first suction nozzle is arranged radially outward of the driving nozzle and wherein the nozzle appliance is designed such that a fluid flow through the driving nozzle drives a fluid flow through the first suction nozzle.
  • the invention also relates to a jet pump comprising a corresponding nozzle appliance.
  • Jet pumps are used for generating a secondary fluid flow by means of a primary driving fluid flow.
  • the primary driving fluid is accelerated by means of e.g. a pump and guided such that it comes into contact with a secondary fluid.
  • a velocity and pressure gradient between the two flu ids ensures that the second fluid is accelerated by the first fluid flow. Therefore, in jet pumps, the second fluid flow is driven by the first fluid flow.
  • Jet pumps may be designed as single stage or multiple-stage jet pumps comprising a plurality of pump stages and nozzles.
  • a major disadvantage of jet pumps is their low efficiency resulting from the mixing of a high velocity jet of the primary driving fluid with a nearly stagnant second ary fluid.
  • the object of the present invention is therefore to provide an improved jet pump and an im proved jet pump nozzle geometry, which exhibit superior efficiencies compared to known jet pumps and jet pump nozzle geometries.
  • a nozzle appliance for a jet pump comprising a driving nozzle and a first suction nozzle, wherein the first suction nozzle is ar ranged radially outward of the driving nozzle and wherein the nozzle appliance is designed such that a fluid flow through the driving nozzle drives a fluid flow through the first suction nozzle.
  • a driving nozzle outlet may be situated close enough to a first suction noz zle outlet such that the low pressure and high velocity fluid flow of the driving nozzle may inter act with the fluid of the first suction nozzle.
  • the first suction nozzle may be positioned such that the shear stress at the interface between the jet and the suction mass or the fluid flow through the driving nozzle and the fluid flow through the first or further suction nozzles is reduced.
  • This is related to the fact that the above- defined shear stress is the product of fluid viscosity and the velocity gradient. The latter may be very large in jet pumps known from the art. High shear stresses lead to the generation of turbu lences, which in return lead to dissipation of primary energy, which is the reason for the low effi ciency of known jet pumps.
  • the jet pump and nozzle appliance of the present invention provide for enhanced jet pump efficiency, as the shear stresses are reduced when the mixing of the two or more mass flows or fluid flows is induced.
  • the nozzle appliance can be designed such that the first suction nozzle is arranged concentrically around the driving nozzle and/or that the first suc tion nozzle comprises an axisymmetric volume, such as a toroidal volume.
  • the driving nozzle and/or the first suction nozzle may comprise nozzle wall sections, which feature rotational sym metry, in particular around a central axis of one of the nozzles or of both of the nozzles.
  • the nozzle appliance can be designed such that a first mixing tube is provided downstream of the driving nozzle and the first suction nozzle.
  • the first mixing tube may be connected to an outside wall of the first suction nozzle.
  • the first mixing tube and the outside wall of the first suction nozzle may be made from one piece.
  • the first mixing tube, the driving nozzle and the first suction nozzle may be arranged co axially to each other.
  • the nozzle appliance can be designed such that the first mixing tube comprises a first diffusor stage at the downstream end of the first mixing tube.
  • the first diffusor stage may feature a larger cross-sectional area than a section of the first mixing tube which is positioned further upstream of the first diffusor stage.
  • the first dif fusor stage of the first mixing tube may be arranged concentrically to other portions of the first mixing tube and/or the driving nozzle and/or the first suction nozzle.
  • the nozzle appliance can be de signed such that a second suction nozzle is arranged downstream of the first mixing tube, wherein the nozzle appliance is designed such that a fluid flow through the first mixing tube drives a fluid through the second suction nozzle and/or wherein the second suction nozzle is ar ranged concentrically around the first mixing tube and/or wherein the second suction nozzle comprises an axisymmetric volume.
  • the design and functioning of the second suction nozzle may comprise features such as the ones described with respect to the first suction nozzle where applicable.
  • the second suction nozzle may be located close enough to the outlet of the first mixing tube such that the low pressure and high velocity fluid flow of the first mixing tube may interact with the fluid of the second suction nozzle.
  • the second suction nozzle may be posi tioned such that the shear stress at the interface between the jet and the suction mass or the fluid flow through the first mixing tube and the fluid flow through the second suction nozzle is re depictd.
  • the nozzle appliance can be designed such that a second mixing tube is provided downstream of the first mixing tube and the second suction nozzle.
  • the second mixing tube may be connected to an outside wall of the second suc tion nozzle.
  • the second mixing tube and the outside wall of the second suction noz zle may be made from one piece.
  • the second mixing tube, the first mixing tube, the driving noz zle and/or the first and second suction nozzles may be arranged coaxially to each other.
  • the nozzle appliance can be designed such that the second mixing tube comprises a second diffusor stage at the downstream end of the second mixing tube.
  • the second diffusor stage may feature a larger cross-sectional area than a section of the second mixing tube which is positioned further upstream of the second dif fusor stage.
  • the second diffusor stage may be arranged concentrically to other portions of the second mixing tube and/or the driving nozzle and/or the first and/or second suction nozzle.
  • the nozzle appliance can be designed such that a first fluid flows through the driving nozzle and a second fluid flows through the first and/or the second suction nozzle, wherein the first and second fluids are the same kinds of flu ids or wherein the first and second fluids are different kinds of fluids.
  • the first fluid flowing through the driving nozzle may be regarded as the driving fluid.
  • the first and second fluid may be provided from the same fluid source or from different and separated fluid sources.
  • the nozzle appliance can be designed such that the first fluid is a gas and the second fluid is a gas and/or that the second fluid is a liq uid.
  • the present nozzle design may be used with any suitable combination of liquids and/or gases.
  • air, fuel vapours, combustions gases and mixtures thereof may be chosen as either of the fluids.
  • the present invention is also directed at a jet pump comprising at least one nozzle appliance according to any of claims 1 to 9.
  • the term jet pump may be understood to comprise further components in addition to the nozzle appliance.
  • Such further components may include a power source, a pressure source, a control device, electronic connections, fluid connections, one or more fluid sources and/or fluid conduits.
  • Fig. 1 nozzle appliance comprising one driving nozzle and two suction nozzles;
  • Figs. 2a, 2b schematic view of a nozzle appliance according to the state of the art.
  • Figs. 3a, 3b schematic view of a nozzle appliance according to the invention.
  • Figure 1 shows a nozzle appliance for a jet pump.
  • the term jet pump may be understood in a broad sense and may comprise any further additional components other than the actual nozzle geometry shown in figure 1.
  • the nozzle appliance comprises a driving nozzle 10 and a first suc tion nozzle 1 , wherein the first suction nozzle 1 is arranged radially outward of the driving nozzle 10 and wherein the nozzle appliance is designed such that a fluid flow through the driving noz zle 10 drives a fluid through the first suction nozzle 1.
  • the nozzle appliance may be arranged around a centreline C. In particular, the nozzle appliance may be at least partially symmetrical about centreline C.
  • the first suction nozzle 1 may be arranged concentrically around the driving nozzle 10.
  • the driving nozzle 10 may have a circular cross section and comprise cylindrical conduit portions. Alternatively or additionally, the driving nozzle 10 may comprise non-cylindrical conduit portions.
  • the first suction nozzle 1 may comprise an axisymmetric volume or axisymmetric conduit por tions.
  • the conduit portions of the driving nozzle 10 may be positioned at least partially within the conduit portions of the first suction nozzle 1. In these cases, the nozzle appliance may exhibit rotational symmetry around centreline C at least at some positions along the centreline C.
  • the nozzle appliance may exhibit reflectional symmetry about a plane which com prises centreline C and which is perpendicular to the plane of projection of figure 1.
  • the suction nozzle 1 and the driving nozzle 10 may comprise e.g. cuboid or near conduit por tions.
  • the nozzle appliance may not exhibit reflectional symmetry about the above defined plane but may still comprise conduit portions of exclusively or at least partially cuboid geometries.
  • the term conduit portion may be presently understood to refer to conduit portions, which are bound by solid walls in a radial direction. The solid walls may surround the conduit portions completely in a circumferential direction of the conduit portions.
  • the conduit portions of the driving nozzle 10 and the first suction nozzle 1 may be at least par tially separated by a first wall 11.
  • the first wall 11 may comprise a conical portion and at least one cylindrical portion connected directly to the conical portion.
  • the right end or downstream end of the first wall 11 may be regarded as the exit portion of the driving nozzle 10, in which the first fluid of the driving nozzle 10 meets the second fluid of the first suction nozzle 1 and the two fluids interact with each other, such that the second fluid is driven by the first fluid.
  • the inside of the first wall 11 may surround the driving nozzle 10 com pletely and therefore on its own define the cross-section area and shape of the driving nozzle 10.
  • the outside of the first wall 11 may define the inside boundary of the first suction nozzle 1.
  • the inside and outside of the first wall 11 may comprise surfaces which are parallel or nearly parallel to each other.
  • the first wall 11 may comprise at least one cylindrical portion or a portion with constant cross-sectional area along the flow direction.
  • first wall 11 which is the furthest downstream portion or close to the furthest downstream portion of the first wall 11.
  • This close alignment of these two sides of the first 11 wall ensures that the streamlines of the flow through the driving nozzle 10 and the streamlines of the flow through the first suction nozzle 1 are parallel or near parallel to each other when flowing together or meeting each other.
  • a first mixing tube 3 Downstream of the exit portion of the driving nozzle 10 a first mixing tube 3 is provided.
  • the fluid flow direction is indicated by the three arrows to the left and above the nozzle appliance.
  • the general flow direction in figure 1 is from left to right. Downstream positions of components are therefore to be found on the right sides of the compo nents of the nozzle appliance in figure 1.
  • the first mixing tube 3 is hence provided downstream of the driving nozzle 10 and the first suc tion nozzle 1.
  • the diameter or cross-sectional area of the mixing tube 3 may be selected such that it may accommodate the combined volume flow of the driving nozzle 10 and the first suc tion nozzle 1.
  • the first mixing tube 3 may be bound by a second wall 32 and/or the first mixing tube 3 may comprise a partially or entirely cylindrical conduit portion.
  • the length of the first mixing tube 3 may be selected to be 2 to 5 times the width or the diameter of the mixing tube 3. In particular, the length of the mixing tube 3 may be selected to be 2,5 to 4 times the width or the diameter of the mixing tube 3.
  • the first mixing tube 3 may be designed such that it comprises a first diffusor stage 31 at the downstream end of the first mixing tube 3.
  • the first diffusor stage 31 may be of a greater cross- sectional area, diameter or width than other, in particular upstream, portions of the first mixing tube 3.
  • the first diffusor stage 31 may be the most downstream portion or may be close to the most downstream portion of the first mixing tube 3.
  • the first mixing tube 3 and the first diffusor stage 31 may be formed integrally by the second wall 32.
  • the first diffusor stage 31 may be close to or may be part of a second suction nozzle 2, which is arranged downstream of the first mixing tube 3, wherein the nozzle appliance is designed such that a fluid flow through the first mixing tube 3 drives a fluid through the second suction nozzle 2 and/or wherein the second suction nozzle 2 is arranged concentrically around the first mixing tube 3 and/or wherein the second suction nozzle 2 comprises an axisymmetric volume, bound by inner and outer walls.
  • the present nozzle appliance may be a one or more stage nozzle appliance, comprising a multitude of suction nozzles 1 , 2 and/or driving nozzles 10.
  • the most downstream portion of the first mixing tube 3, in particular the exit portion of the first mixing tube 3 may be regarded as another driving nozzle or as a part of another driv ing nozzle for driving fluid through the second suction nozzle 2.
  • the geometry of the second suction nozzle 2 may correspond to the geometry of the first suc tion nozzle 1 in that it may exhibit rotational symmetry around centreline C or reflective sym metry in analogy to the reflective symmetry of the first suction nozzle 1 described above. Alter natively, a non-symmetric embodiment is also possible as described above. Furthermore, the walls bounding the second suction nozzle 2, i.e. the second wall 32 on the inside of the second suction nozzle 2 and another wall on the outside of the second suction nozzle 2 may be ori ented such that they align the flow through the second suction nozzle 2 closely to the flow through the first mixing tube 3.
  • the second suction nozzle 2 may be provided such that the velocity vectors of the fluid flow through the second suction nozzle 2 approach the ve locity vectors of the fluid flow through the first mixing tube 3 in direction and magnitude.
  • the bounding walls of the second suction nozzle 2 may be therefore parallel and/or angled to the flow direction through the mixing tube 3 such that the flow through the first mixing tube 3 and the flow through the second suction nozzle 2 mix together with only minimal losses.
  • a second mixing tube 4 may be provided downstream of the first mixing tube 3 and the second suction nozzle 2.
  • the second mixing tube 4 may comprise cylindrical conduit portions and/or a second diffusor stage 41 at the downstream end of the second mixing tube 4.
  • the downstream end of the second mixing tube 4 may be connected or connectable to a fluid conduit.
  • the driving nozzle 10 is flowed through by a first fluid and the first suction nozzle 1 and/or the second suction nozzle 2 are flowed through by a sec ond fluid, wherein the first and second fluids are the same kinds of fluids or wherein the first and second fluids are different kinds of fluids.
  • the first fluid of the driving nozzle 10 drives the fluids flowing through the suction nozzles 1, 2 and the fluids may be gases and/or liquids.
  • the fist suction nozzle 1, or the two or more suction nozzles 1, 2 may be annular or near annu lar nozzles surrounding the circular driving nozzle 10 or surrounding further driving nozzles at least partially.
  • the driving nozzle 10 may be surrounded concentrically or in a different way.
  • the driving nozzle 10 may be a driving air nozzle.
  • the nozzle appliance may be used together with a turbo charger of a combustion engine. In this case, the nozzle appliance may be regarded as part of a jet pump for pumping gases from e.g. a fuel tank and into the combustion engine.
  • the nozzles of the present invention may be designed such that the flow velocities and/or the flow directions of neighbouring nozzles are as similar as possible.
  • the nozzles may be designed such that the flow directions and/or velocities of the first fluid flow exiting the driving nozzle 10 are as similar as possible to the second fluid flow exiting the first and/or second suc tion nozzles 1, 2.
  • the present nozzle appliance and corresponding jet pumps in effect provide at least one addi tional suction nozzle 1, 2, increasing the flow velocity of the suction flow before it mixes with the driving flow.
  • the additional suctions nozzle 1 , 2 effectively reduces the generation of turbu lences during mixing of the at least two fluid flows, i.e. the first and second fluid flows. As a re sult, power and efficiency of the pump are increased.
  • Power is supplied to corresponding jet pumps in form of a driving mass flow, which is acceler ated in a driving nozzle and which correspondingly generates a fluid jet of high velocity and low pressures.
  • the emerging low pressure is utilized to draw a suction mass flow into the pump or nozzle appliance, which mixes with the driving flow i.e. the first fluid flow.
  • Driving mass flux or first fluid flow and suction mass flux or second fluid flow leave the pump or nozzle appliance af ter passing one or more diffusor stages 31 , 41, which increase the pressure of the flow.
  • jet pumps are their simple design with no need for moving parts.
  • Major disadvantages include the low efficiency of such pumps resulting from the mixing of a high ve locity jet with a nearly stagnant fluid.
  • FIG. 2a shows a schematic view of a typical jet pump flow configuration as known from the art.
  • Figure 2b shows a simplified representation of the corresponding fluid flow.
  • a jet of high velocity is generated by a driving nozzle 10, which draws in the suction mass flow, which typically has a very low velocity.
  • Figure 2b is an idealized representation of a typical jet pump flow.
  • the low velocity suction mass flow is indicated by the short horizontal arrows. It mixes with the high velocity jet indicated by long horizontal arrows.
  • the high velocity gradient shown leads to high shear stresses.
  • the flow shown in figure 2b only accounts for the flow component in the direction of the jet, i.e. the horizontal direction.
  • the latter is usually very large due to the high difference in the velocities of the two fluid flows.
  • High shear stresses lead to the generation of turbulences, which in return lead to dissipa tion of primary energy, which is the reason for the low efficiency of jet pumps.
  • a more efficient jet pump requires a reduction of the shear stress induced by the mixing of the two mass flows. As the jet velocity is dictated by the necessary pumping pressure, the only way to reduce the shear stress at the interface is by increasing the flow velocity of the suction flow in direction of the jet flow.
  • Figures 3a and 3b show a jet pump flow configuration in which the suction flow is accelerated before mixing with the jet, thereby decreasing the velocity gradient. This reduces the shear stresses and therefore the amount of generated turbulences and dissipated energy. As a result, less energy is lost, and the jet pump is more efficient.
  • the jet pump or nozzle appli ance comprises the driving nozzle 10 and the first suction nozzle 1 for the suction flow.
  • Figure 3b shows an idealized representation of the corresponding flow.
  • the suction flow velocity is in dicated by the shorter horizontal arrows and the jet flow velocity is indicated by the longer hori zontal arrows. As can be seen, the difference in length and therefore velocity is smaller than in the situation shown in figure 2b.
  • the flow shown in figure 3b only accounts for the flow component in the direction of the jet, i.e. the hori zontal direction.
  • the suction nozzles 1, 2 may be designed to direct the second fluid flow such that it approaches the first fluid flow in a parallel direction to it or at a very small angle.
  • the suction nozzles 1, 2 may comprise correspondingly angled bounda ries.
  • the present invention is of particular use for the ventilation of crankcases and fuel tanks of vehi cles. Due to blow-by and fuel evaporation, these components need to be ventilated by use of corresponding jet pumps in order to achieve current emission regulations.
  • the air provided to a combustion engine may be used as a driving fluid or first fluid.
  • the air provided may be compressed air e.g. from a turbocharger or a compressor.
  • the present invention provides highly performant means for ventilating these components at idle engine and full throttle operation re sulting in low and high driving pressures.
  • the present invention provides for jet pumps with low consumption of driving air or driving fluid at full throttle of the engine.
  • the invention is not limited to any of the above-described embodiments or features.
  • the inven tion may comprise various additions to or modification of the described embodiments.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

The present invention relates to a nozzle appliance for a jet pump, comprising a driving nozzle and a first suction nozzle, wherein the first suction nozzle is arranged radially outward of the driving nozzle and wherein the nozzle appliance is designed such that a fluid flow through the driving nozzle drives a fluid flow through the first suction nozzle. The invention also relates to a jet pump comprising a corresponding nozzle appliance.

Description

Nozzle appliance for a jet pump and jet pump
The present invention relates to a nozzle appliance for a jet pump, comprising a driving nozzle and a first suction nozzle, wherein the first suction nozzle is arranged radially outward of the driving nozzle and wherein the nozzle appliance is designed such that a fluid flow through the driving nozzle drives a fluid flow through the first suction nozzle. The invention also relates to a jet pump comprising a corresponding nozzle appliance.
Jet pumps are used for generating a secondary fluid flow by means of a primary driving fluid flow. The primary driving fluid is accelerated by means of e.g. a pump and guided such that it comes into contact with a secondary fluid. A velocity and pressure gradient between the two flu ids ensures that the second fluid is accelerated by the first fluid flow. Therefore, in jet pumps, the second fluid flow is driven by the first fluid flow.
Jet pumps may be designed as single stage or multiple-stage jet pumps comprising a plurality of pump stages and nozzles. A major disadvantage of jet pumps is their low efficiency resulting from the mixing of a high velocity jet of the primary driving fluid with a nearly stagnant second ary fluid. The object of the present invention is therefore to provide an improved jet pump and an im proved jet pump nozzle geometry, which exhibit superior efficiencies compared to known jet pumps and jet pump nozzle geometries.
This object is achieved by a nozzle appliance according to claim 1 and by a jet pump according to claim 10, said jet pump comprising at least one such nozzle appliance. Advantageous em bodiments of the invention are subject of the dependent claims.
According to the invention, a nozzle appliance for a jet pump is provided, said nozzle appliance comprising a driving nozzle and a first suction nozzle, wherein the first suction nozzle is ar ranged radially outward of the driving nozzle and wherein the nozzle appliance is designed such that a fluid flow through the driving nozzle drives a fluid flow through the first suction nozzle. In a simple embodiment, a driving nozzle outlet may be situated close enough to a first suction noz zle outlet such that the low pressure and high velocity fluid flow of the driving nozzle may inter act with the fluid of the first suction nozzle.
The first suction nozzle may be positioned such that the shear stress at the interface between the jet and the suction mass or the fluid flow through the driving nozzle and the fluid flow through the first or further suction nozzles is reduced. This is related to the fact that the above- defined shear stress is the product of fluid viscosity and the velocity gradient. The latter may be very large in jet pumps known from the art. High shear stresses lead to the generation of turbu lences, which in return lead to dissipation of primary energy, which is the reason for the low effi ciency of known jet pumps. The jet pump and nozzle appliance of the present invention provide for enhanced jet pump efficiency, as the shear stresses are reduced when the mixing of the two or more mass flows or fluid flows is induced.
In a preferred embodiment of the invention, the nozzle appliance can be designed such that the first suction nozzle is arranged concentrically around the driving nozzle and/or that the first suc tion nozzle comprises an axisymmetric volume, such as a toroidal volume. The driving nozzle and/or the first suction nozzle may comprise nozzle wall sections, which feature rotational sym metry, in particular around a central axis of one of the nozzles or of both of the nozzles.
In another preferred embodiment of the invention, the nozzle appliance can be designed such that a first mixing tube is provided downstream of the driving nozzle and the first suction nozzle. The first mixing tube may be connected to an outside wall of the first suction nozzle. In particu lar, the first mixing tube and the outside wall of the first suction nozzle may be made from one piece. The first mixing tube, the driving nozzle and the first suction nozzle may be arranged co axially to each other. In a particularly preferred embodiment of the invention, the nozzle appliance can be designed such that the first mixing tube comprises a first diffusor stage at the downstream end of the first mixing tube. The first diffusor stage may feature a larger cross-sectional area than a section of the first mixing tube which is positioned further upstream of the first diffusor stage. The first dif fusor stage of the first mixing tube may be arranged concentrically to other portions of the first mixing tube and/or the driving nozzle and/or the first suction nozzle.
In another particularly preferred embodiment of the invention, the nozzle appliance can be de signed such that a second suction nozzle is arranged downstream of the first mixing tube, wherein the nozzle appliance is designed such that a fluid flow through the first mixing tube drives a fluid through the second suction nozzle and/or wherein the second suction nozzle is ar ranged concentrically around the first mixing tube and/or wherein the second suction nozzle comprises an axisymmetric volume. The design and functioning of the second suction nozzle may comprise features such as the ones described with respect to the first suction nozzle where applicable.
In particular, the second suction nozzle may be located close enough to the outlet of the first mixing tube such that the low pressure and high velocity fluid flow of the first mixing tube may interact with the fluid of the second suction nozzle. The second suction nozzle may be posi tioned such that the shear stress at the interface between the jet and the suction mass or the fluid flow through the first mixing tube and the fluid flow through the second suction nozzle is re duced.
In a particularly preferred embodiment of the invention, the nozzle appliance can be designed such that a second mixing tube is provided downstream of the first mixing tube and the second suction nozzle. The second mixing tube may be connected to an outside wall of the second suc tion nozzle. In particular, the second mixing tube and the outside wall of the second suction noz zle may be made from one piece. The second mixing tube, the first mixing tube, the driving noz zle and/or the first and second suction nozzles may be arranged coaxially to each other.
In a particularly preferred embodiment of the invention, the nozzle appliance can be designed such that the second mixing tube comprises a second diffusor stage at the downstream end of the second mixing tube. The second diffusor stage may feature a larger cross-sectional area than a section of the second mixing tube which is positioned further upstream of the second dif fusor stage. The second diffusor stage may be arranged concentrically to other portions of the second mixing tube and/or the driving nozzle and/or the first and/or second suction nozzle. In a particularly preferred embodiment of the invention, the nozzle appliance can be designed such that a first fluid flows through the driving nozzle and a second fluid flows through the first and/or the second suction nozzle, wherein the first and second fluids are the same kinds of flu ids or wherein the first and second fluids are different kinds of fluids. The first fluid flowing through the driving nozzle may be regarded as the driving fluid. The first and second fluid may be provided from the same fluid source or from different and separated fluid sources.
In a particularly preferred embodiment of the invention, the nozzle appliance can be designed such that the first fluid is a gas and the second fluid is a gas and/or that the second fluid is a liq uid. In general, the present nozzle design may be used with any suitable combination of liquids and/or gases. In cases in which a gas is used as one or both of the fluids, air, fuel vapours, combustions gases and mixtures thereof may be chosen as either of the fluids.
The present invention is also directed at a jet pump comprising at least one nozzle appliance according to any of claims 1 to 9. The term jet pump may be understood to comprise further components in addition to the nozzle appliance. Such further components may include a power source, a pressure source, a control device, electronic connections, fluid connections, one or more fluid sources and/or fluid conduits.
Further details and advantages of the invention are described with reference to the embodi ments shown in the figures.
Fig. 1: nozzle appliance comprising one driving nozzle and two suction nozzles;
Figs. 2a, 2b: schematic view of a nozzle appliance according to the state of the art; and
Figs. 3a, 3b: schematic view of a nozzle appliance according to the invention.
Figure 1 shows a nozzle appliance for a jet pump. The term jet pump may be understood in a broad sense and may comprise any further additional components other than the actual nozzle geometry shown in figure 1. The nozzle appliance comprises a driving nozzle 10 and a first suc tion nozzle 1 , wherein the first suction nozzle 1 is arranged radially outward of the driving nozzle 10 and wherein the nozzle appliance is designed such that a fluid flow through the driving noz zle 10 drives a fluid through the first suction nozzle 1. The nozzle appliance may be arranged around a centreline C. In particular, the nozzle appliance may be at least partially symmetrical about centreline C.
The first suction nozzle 1 may be arranged concentrically around the driving nozzle 10. The driving nozzle 10 may have a circular cross section and comprise cylindrical conduit portions. Alternatively or additionally, the driving nozzle 10 may comprise non-cylindrical conduit portions. The first suction nozzle 1 may comprise an axisymmetric volume or axisymmetric conduit por tions. The conduit portions of the driving nozzle 10 may be positioned at least partially within the conduit portions of the first suction nozzle 1. In these cases, the nozzle appliance may exhibit rotational symmetry around centreline C at least at some positions along the centreline C.
Alternatively, the nozzle appliance may exhibit reflectional symmetry about a plane which com prises centreline C and which is perpendicular to the plane of projection of figure 1. In this case, the suction nozzle 1 and the driving nozzle 10 may comprise e.g. cuboid or near conduit por tions. Furthermore, the nozzle appliance may not exhibit reflectional symmetry about the above defined plane but may still comprise conduit portions of exclusively or at least partially cuboid geometries. The term conduit portion may be presently understood to refer to conduit portions, which are bound by solid walls in a radial direction. The solid walls may surround the conduit portions completely in a circumferential direction of the conduit portions.
The conduit portions of the driving nozzle 10 and the first suction nozzle 1 may be at least par tially separated by a first wall 11. The first wall 11 may comprise a conical portion and at least one cylindrical portion connected directly to the conical portion.
The right end or downstream end of the first wall 11 may be regarded as the exit portion of the driving nozzle 10, in which the first fluid of the driving nozzle 10 meets the second fluid of the first suction nozzle 1 and the two fluids interact with each other, such that the second fluid is driven by the first fluid. The inside of the first wall 11 may surround the driving nozzle 10 com pletely and therefore on its own define the cross-section area and shape of the driving nozzle 10. The outside of the first wall 11 may define the inside boundary of the first suction nozzle 1. The inside and outside of the first wall 11 may comprise surfaces which are parallel or nearly parallel to each other. In particular, the first wall 11 may comprise at least one cylindrical portion or a portion with constant cross-sectional area along the flow direction. This applies in particular to the portion of the first wall 11 which is the furthest downstream portion or close to the furthest downstream portion of the first wall 11. This close alignment of these two sides of the first 11 wall ensures that the streamlines of the flow through the driving nozzle 10 and the streamlines of the flow through the first suction nozzle 1 are parallel or near parallel to each other when flowing together or meeting each other.
Downstream of the exit portion of the driving nozzle 10 a first mixing tube 3 is provided. The fluid flow direction is indicated by the three arrows to the left and above the nozzle appliance. Around and close to the centreline C, the general flow direction in figure 1 is from left to right. Downstream positions of components are therefore to be found on the right sides of the compo nents of the nozzle appliance in figure 1. The first mixing tube 3 is hence provided downstream of the driving nozzle 10 and the first suc tion nozzle 1. The diameter or cross-sectional area of the mixing tube 3 may be selected such that it may accommodate the combined volume flow of the driving nozzle 10 and the first suc tion nozzle 1.
The first mixing tube 3 may be bound by a second wall 32 and/or the first mixing tube 3 may comprise a partially or entirely cylindrical conduit portion. The length of the first mixing tube 3 may be selected to be 2 to 5 times the width or the diameter of the mixing tube 3. In particular, the length of the mixing tube 3 may be selected to be 2,5 to 4 times the width or the diameter of the mixing tube 3.
The first mixing tube 3 may be designed such that it comprises a first diffusor stage 31 at the downstream end of the first mixing tube 3. The first diffusor stage 31 may be of a greater cross- sectional area, diameter or width than other, in particular upstream, portions of the first mixing tube 3. The first diffusor stage 31 may be the most downstream portion or may be close to the most downstream portion of the first mixing tube 3. The first mixing tube 3 and the first diffusor stage 31 may be formed integrally by the second wall 32.
The first diffusor stage 31 may be close to or may be part of a second suction nozzle 2, which is arranged downstream of the first mixing tube 3, wherein the nozzle appliance is designed such that a fluid flow through the first mixing tube 3 drives a fluid through the second suction nozzle 2 and/or wherein the second suction nozzle 2 is arranged concentrically around the first mixing tube 3 and/or wherein the second suction nozzle 2 comprises an axisymmetric volume, bound by inner and outer walls.
As shown in the embodiment of figure 1 , the present nozzle appliance may be a one or more stage nozzle appliance, comprising a multitude of suction nozzles 1 , 2 and/or driving nozzles 10. Hence, the most downstream portion of the first mixing tube 3, in particular the exit portion of the first mixing tube 3 may be regarded as another driving nozzle or as a part of another driv ing nozzle for driving fluid through the second suction nozzle 2.
The geometry of the second suction nozzle 2 may correspond to the geometry of the first suc tion nozzle 1 in that it may exhibit rotational symmetry around centreline C or reflective sym metry in analogy to the reflective symmetry of the first suction nozzle 1 described above. Alter natively, a non-symmetric embodiment is also possible as described above. Furthermore, the walls bounding the second suction nozzle 2, i.e. the second wall 32 on the inside of the second suction nozzle 2 and another wall on the outside of the second suction nozzle 2 may be ori ented such that they align the flow through the second suction nozzle 2 closely to the flow through the first mixing tube 3. In particular, the second suction nozzle 2 may be provided such that the velocity vectors of the fluid flow through the second suction nozzle 2 approach the ve locity vectors of the fluid flow through the first mixing tube 3 in direction and magnitude. The bounding walls of the second suction nozzle 2 may be therefore parallel and/or angled to the flow direction through the mixing tube 3 such that the flow through the first mixing tube 3 and the flow through the second suction nozzle 2 mix together with only minimal losses.
A second mixing tube 4 may be provided downstream of the first mixing tube 3 and the second suction nozzle 2. The second mixing tube 4 may comprise cylindrical conduit portions and/or a second diffusor stage 41 at the downstream end of the second mixing tube 4. The downstream end of the second mixing tube 4 may be connected or connectable to a fluid conduit.
During operation of the nozzle appliance, the driving nozzle 10 is flowed through by a first fluid and the first suction nozzle 1 and/or the second suction nozzle 2 are flowed through by a sec ond fluid, wherein the first and second fluids are the same kinds of fluids or wherein the first and second fluids are different kinds of fluids. The first fluid of the driving nozzle 10 drives the fluids flowing through the suction nozzles 1, 2 and the fluids may be gases and/or liquids.
The fist suction nozzle 1, or the two or more suction nozzles 1, 2 may be annular or near annu lar nozzles surrounding the circular driving nozzle 10 or surrounding further driving nozzles at least partially. The driving nozzle 10 may be surrounded concentrically or in a different way. The driving nozzle 10 may be a driving air nozzle. The nozzle appliance may be used together with a turbo charger of a combustion engine. In this case, the nozzle appliance may be regarded as part of a jet pump for pumping gases from e.g. a fuel tank and into the combustion engine.
The nozzles of the present invention may be designed such that the flow velocities and/or the flow directions of neighbouring nozzles are as similar as possible. In particular, the nozzles may be designed such that the flow directions and/or velocities of the first fluid flow exiting the driving nozzle 10 are as similar as possible to the second fluid flow exiting the first and/or second suc tion nozzles 1, 2.
The present nozzle appliance and corresponding jet pumps in effect provide at least one addi tional suction nozzle 1, 2, increasing the flow velocity of the suction flow before it mixes with the driving flow. The additional suctions nozzle 1 , 2 effectively reduces the generation of turbu lences during mixing of the at least two fluid flows, i.e. the first and second fluid flows. As a re sult, power and efficiency of the pump are increased.
Power is supplied to corresponding jet pumps in form of a driving mass flow, which is acceler ated in a driving nozzle and which correspondingly generates a fluid jet of high velocity and low pressures. The emerging low pressure is utilized to draw a suction mass flow into the pump or nozzle appliance, which mixes with the driving flow i.e. the first fluid flow. Driving mass flux or first fluid flow and suction mass flux or second fluid flow leave the pump or nozzle appliance af ter passing one or more diffusor stages 31 , 41, which increase the pressure of the flow.
One main advantage of jet pumps is their simple design with no need for moving parts. Major disadvantages include the low efficiency of such pumps resulting from the mixing of a high ve locity jet with a nearly stagnant fluid.
Figure 2a shows a schematic view of a typical jet pump flow configuration as known from the art. Figure 2b shows a simplified representation of the corresponding fluid flow. As shown in fig ure 2a, a jet of high velocity is generated by a driving nozzle 10, which draws in the suction mass flow, which typically has a very low velocity.
Figure 2b is an idealized representation of a typical jet pump flow. The low velocity suction mass flow is indicated by the short horizontal arrows. It mixes with the high velocity jet indicated by long horizontal arrows. The high velocity gradient shown leads to high shear stresses. The flow shown in figure 2b only accounts for the flow component in the direction of the jet, i.e. the horizontal direction.
The shear stress t at the interface between jet and suction mass flow or between the first and second fluid flow, respectively, increases with the velocity gradient of the corresponding fluid flow. The latter is usually very large due to the high difference in the velocities of the two fluid flows. High shear stresses lead to the generation of turbulences, which in return lead to dissipa tion of primary energy, which is the reason for the low efficiency of jet pumps. A more efficient jet pump requires a reduction of the shear stress induced by the mixing of the two mass flows. As the jet velocity is dictated by the necessary pumping pressure, the only way to reduce the shear stress at the interface is by increasing the flow velocity of the suction flow in direction of the jet flow.
Figures 3a and 3b show a jet pump flow configuration in which the suction flow is accelerated before mixing with the jet, thereby decreasing the velocity gradient. This reduces the shear stresses and therefore the amount of generated turbulences and dissipated energy. As a result, less energy is lost, and the jet pump is more efficient. In figure 3a, the jet pump or nozzle appli ance comprises the driving nozzle 10 and the first suction nozzle 1 for the suction flow. Figure 3b shows an idealized representation of the corresponding flow. The suction flow velocity is in dicated by the shorter horizontal arrows and the jet flow velocity is indicated by the longer hori zontal arrows. As can be seen, the difference in length and therefore velocity is smaller than in the situation shown in figure 2b. Therefore, the shear stress is reduced. As before, the flow shown in figure 3b only accounts for the flow component in the direction of the jet, i.e. the hori zontal direction. The suction nozzles 1, 2 may be designed to direct the second fluid flow such that it approaches the first fluid flow in a parallel direction to it or at a very small angle. In order to achieve this effect, the suction nozzles 1, 2 may comprise correspondingly angled bounda ries.
The present invention is of particular use for the ventilation of crankcases and fuel tanks of vehi cles. Due to blow-by and fuel evaporation, these components need to be ventilated by use of corresponding jet pumps in order to achieve current emission regulations. Here, the air provided to a combustion engine may be used as a driving fluid or first fluid. The air provided may be compressed air e.g. from a turbocharger or a compressor. The present invention provides highly performant means for ventilating these components at idle engine and full throttle operation re sulting in low and high driving pressures. At the same time, the present invention provides for jet pumps with low consumption of driving air or driving fluid at full throttle of the engine.
The invention is not limited to any of the above-described embodiments or features. The inven tion may comprise various additions to or modification of the described embodiments.
All of the features and advantages arising from the claims, the description and the drawings, in cluding structural details, spatial arrangements and procedural steps, can be essential to the in vention both, individually and in the most varied of combinations.
Reference numbers
1 first suction nozzle
2 second suction nozzle 3 first mixing tube
4 second mixing tube
10 driving nozzle
11 first wall
31 first diffusor stage 32 second wall
41 second diffusor stage
C centreline

Claims

Claims
1. Nozzle appliance for a jet pump, comprising a driving nozzle (10) and a first suction nozzle (1), wherein the first suction nozzle (1) is arranged radially outward of the driving nozzle (10) and wherein the nozzle appliance is designed such that a fluid flow through the driving noz zle (10) drives a fluid through the first suction nozzle (1).
2. Nozzle appliance according to claim 1, characterized in that the first suction nozzle (1) is ar ranged concentrically around the driving nozzle (10) and/or that the first suction nozzle (1) comprises an axisymmetric volume.
3. Nozzle appliance according to claim 1 or 2, characterized in that a first mixing tube (3) is pro vided downstream of the driving nozzle (10) and the first suction nozzle (1).
4. Nozzle appliance according to claim 3, characterized in that the first mixing tube (3) com prises a first diffusor stage (31) at the downstream end of the first mixing tube (3).
5. Nozzle appliance according to claim 3 or 4, characterized in that a second suction nozzle (2) is arranged downstream of the first mixing tube (3), wherein the nozzle appliance is designed such that a fluid flow through the first mixing tube (3) drives a fluid through the second suc tion nozzle (2) and/or wherein the second suction nozzle (2) is arranged concentrically around the first mixing tube (3) and/or wherein the second suction nozzle (2) comprises an axisymmetric volume.
6. Nozzle appliance according to claim 5, characterized in that a second mixing tube (4) is pro vided downstream of the first mixing tube (3) and the second suction nozzle (2).
7. Nozzle appliance according to claim 6, characterized in that the second mixing tube (4) com prises a second diffusor stage (41) at the downstream end of the second mixing tube (4).
8. Nozzle appliance according to any of the preceding claims, characterized in that a first fluid flows through the driving nozzle and a second fluid flows through the first (1) and/or the sec ond suction nozzle (2), wherein the first and second fluids are the same kinds of fluids or wherein the first and second fluids are different kinds of fluids.
9. Nozzle appliance according to claim 8, characterized in that the first fluid is a gas and the second fluid is a gas and/or that the second fluid is a liquid.
10. Jet pump comprising at least one nozzle appliance according to anyone of claims 1 to 9.
EP21734289.8A 2020-07-10 2021-06-10 Nozzle appliance for a jet pump and jet pump Withdrawn EP4179213A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020118330.5A DE102020118330A1 (en) 2020-07-10 2020-07-10 Nozzle device for a jet pump and jet pump
PCT/EP2021/065702 WO2022008162A1 (en) 2020-07-10 2021-06-10 Nozzle appliance for a jet pump and jet pump

Publications (1)

Publication Number Publication Date
EP4179213A1 true EP4179213A1 (en) 2023-05-17

Family

ID=76601187

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21734289.8A Withdrawn EP4179213A1 (en) 2020-07-10 2021-06-10 Nozzle appliance for a jet pump and jet pump

Country Status (7)

Country Link
US (1) US20230287903A1 (en)
EP (1) EP4179213A1 (en)
JP (1) JP2023533328A (en)
KR (1) KR20230014844A (en)
CN (1) CN115917161A (en)
DE (1) DE102020118330A1 (en)
WO (1) WO2022008162A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114688105A (en) * 2022-04-13 2022-07-01 中国船舶重工集团公司第七一九研究所 Multistage auxiliary pressurizing ship water supply device

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US267022A (en) * 1882-11-07 Steam jet injector and exhauster
US742618A (en) * 1902-03-17 1903-10-27 Eynon Evans Mfg Company Blower.
US1138125A (en) * 1907-09-10 1915-05-04 Expl Des Procedes Westinghouse Leblanc Sa Fluid-ejector.
US1135834A (en) * 1913-01-09 1915-04-13 Campbell Morton Hydraulic air-ejector for vacuum cleaning and other purposes.
US2711284A (en) * 1951-05-08 1955-06-21 Marshall W Phillips Vacuum pump
US3662960A (en) 1966-11-21 1972-05-16 United Aircraft Corp Injector head
DE2410570C2 (en) * 1974-03-06 1982-04-29 Basf Ag, 6700 Ludwigshafen Device for sucking in and compressing gases and mixing them with liquid
CN105736482B (en) * 2010-06-21 2018-04-10 靳北彪 Jet injector with high efficiency
WO2013153096A1 (en) 2012-04-10 2013-10-17 J. Schmalz Gmbh Pneumatic vacuum generator with drive nozzle and receiver nozzle
CN104454670A (en) * 2014-10-22 2015-03-25 江苏振华泵业制造有限公司 Vapor-liquid mixed-pumping type injection pump
DE102015200341A1 (en) * 2015-01-13 2016-07-14 Polytec Plastics Germany Gmbh & Co. Kg Multi-stage suction jet pump
DE102017203877A1 (en) 2017-03-09 2018-09-13 Polytec Plastics Germany Gmbh & Co. Kg Switched suction jet pump

Also Published As

Publication number Publication date
CN115917161A (en) 2023-04-04
US20230287903A1 (en) 2023-09-14
JP2023533328A (en) 2023-08-02
KR20230014844A (en) 2023-01-30
WO2022008162A1 (en) 2022-01-13
DE102020118330A1 (en) 2022-01-13

Similar Documents

Publication Publication Date Title
EP2123863B1 (en) Pre-diffuser for centrifugal compressor
US6877960B1 (en) Lobed convergent/divergent supersonic nozzle ejector system
US7553122B2 (en) Self-aspirated flow control system for centrifugal compressors
US20120228054A1 (en) Noise reduction system with chamber
JP2007292075A (en) Optimized configuration of reverse flow combustion system of gas turbine engine
KR20170102868A (en) Crankcase ventilating evacuator
EP4179213A1 (en) Nozzle appliance for a jet pump and jet pump
EP3073198A1 (en) Integrated dual fuel delivery system
CA2580594C (en) Fuel manifold with reduced losses
US5134855A (en) Air flow diffuser with path splitter to control fluid flow
EP2905227A1 (en) Bifurcated ducts including plenums for stabilizing flow therethrough and exhaust systems including the same
US20190093896A1 (en) Nozzle comprising axial extension for a combustion chamber of an engine
SE539728C2 (en) A compressor arrangement supplying charged air to a combustion engine
US10794402B2 (en) Ejector and a turbo-machine having an ejector
US9212819B2 (en) Swirled fuel injection
US20200263707A1 (en) Jet pump comprising an internal nozzle
US10473114B2 (en) Compressor assembly for a turbocharger
Tamaki et al. Enhancement of centrifugal compressor operating range by control of inlet recirculation with inlet fins
US10036401B2 (en) Recirculating pump inlet
US20210140369A1 (en) Low pressure differential ejector pump utilizing a lobed, axisymmetric nozzle
EP3453622B1 (en) Swirling flow eductor system and method
JP2022189406A (en) Pump device and straightening member
WO2022066701A1 (en) Jet pump and filter assembly
CN113530891A (en) Jet pump
JP2018173039A (en) Gas recirculation device

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20221122

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20230829