US3406632A - Reversible hydraulic apparatus - Google Patents

Reversible hydraulic apparatus Download PDF

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Publication number
US3406632A
US3406632A US577089A US57708966A US3406632A US 3406632 A US3406632 A US 3406632A US 577089 A US577089 A US 577089A US 57708966 A US57708966 A US 57708966A US 3406632 A US3406632 A US 3406632A
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United States
Prior art keywords
vanes
duct
blade
impeller
pump
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Expired - Lifetime
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US577089A
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English (en)
Inventor
Duport Jacques
Martin Gilbert
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Societe Grenobloise dEtudes et dApplications Hydrauliques SA SOGREAH
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Grenobloise Etude Appl
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0055—Rotors with adjustable blades
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
    • B63H25/46—Steering or dynamic anchoring by jets or by rudders carrying jets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/548—Specially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/91—Reversible between pump and motor use

Definitions

  • vanes in each group are inclined radially adjacent to the hydraulic machine and the inclined portions of one group of vanes being similar to the inclined portions of the other group of vanes and such that the vanes in each group can without change operate alternately as upstream vanes for one direction of fluid flow and as downstream vanes for the other direction of fluid flow and can impart to the fluid flow when operating as upstream vanes a swirl varying in intensity across the duct passage.
  • the present invention relates to improvements in that type of hydraulic apparatus which employs two directions of flow in their use, such as hydraulic installations comprising rotating hydraulic machines, pumps, turbines and turbine-pumps of the propeller or Kaplan type, which are utilized with two directions of flow so that they will operate identically in either of two flow directions.
  • apparatus embodying the invention can be employed to advantage, for example, as a hydrojet for propelling or steering a vessel, in which use it is desirable to generate an adjustable and reversible fluid flow such as will cause the jet action to vary continuously, and sometimes rapidly, through a range up to and including a complete reversal of the force produced.
  • the primary purpose of the present invention is to provide improved reversible hydraulic apparatus which is capable of changing from one direction of flow to the other, rapidly and in continuous variation, or progressively, without producing abnormal forces such as would cause damage to the machinery, or dangerous hydraulic phenomena, such as for example, cavitation.
  • Hydrojets embodying the invention are not only capable of propelling and steering vessels, but can be utilized to stablize pitching, rolling andyawing, and to provide an adequate means of controlling the immersion of underwater vessels or platforms.
  • the entire fluid circuit is designed to operate at high efficiencies and to produce a powerful thrust in either flow direction.
  • the operation of such apparatus as a whole can be made perfectly symmetrical, that is to say, capable of producing equal thrusts and working at equal efficiencies in opposite flow directions. Its design also enables continuous, and if necessaryy rapid, thrust variations to be achieved, ranging from maximum thrust in one direction, to maximum thrust in the opposite direction.
  • the hydraulic duct of an apparatus embodying the invention comprises the following basic components:
  • the pump is connected to the aforesaid inlet and discharge orifices by ducts, the shape and length of which may depend on requirements arising from the installation of the apparatus.
  • ducts should always be designed to provide for the lowest possible loss of head in order neither to upset the velocity and pressure distribution at the pump intake, nor to cause swirl or to interfere in any way with flow conditions in the discharge, especially in the case of hydrojets.
  • Reversal of the direction of fluid flow may be achieved in any one of the following manners, or by a combination of the same;
  • the pump motor may have a single direction of rotation.
  • FIG. 1 is a schematic vertical sectional view of reversible hydraulic apparatus embodying the invention and illustrates the manner in which such apparatus may be utilized as a hydrojet in a ship;
  • FIG. 2 is an enlarged detailed view of one of the inlet and discharge orifices shown in FIG. 1;
  • FIG. 3 is a horizontal sectional view showing an alternative form of inlet and discharge orifice
  • FIG. 4 is a longitudinal or vertical sectional view of the central portion of a reversible axial pump constituted to accomplish thrust reversal by reversing the direction of rotation of the pump, and if necessary, to accomplish thrust variation by controlling the pump motor speech
  • FIG. 5 is a vertical sectional view of the impeller blade shown in FIG. 4, the distance away from the impeller hub periphery;
  • FIG. 6 is a view similar to FIG. 5 but showing a section taken near the blade tip
  • FIG. 7 is a view similar to that of FIG. 4 of areversible axial pump constructed to accomplish thrust reversal, and if need be, thrust variations, by variation of the angular blade position;
  • FIG. 8 is a vertical sectional view of the impeller blade shown in FIG. 7, the section 'beingtaken a short distance away from the impeller hu'b periphery; and i FIG. 9 is a view similar to FIG.'8, but showing a section taken near the blade tip.
  • V v is a vertical sectional view of the impeller blade shown in FIG. 7, the section 'beingtaken a short distance away from the impeller hu'b periphery; and i FIG. 9 is a view similar to FIG.'8, but showing a section taken near the blade tip.
  • the hydrojet shown in FIG. 1 of the drawings is constructed and arranged to produce a reaction force acting in either'direction'along the horizontal axis X-X.
  • the inlet and dischargeorifices '1 at the ends of the hydraulic ductof the hydrojet are positioned in the ships sides 2 as shown, and are connected to the pump casing 3 forming the central portion of such duct by straight duct sections 4.
  • the duct opening within the pump casing 3 is formed by the latter and the faired or streamlined bulb casing 5 extending longitudinally centerally of such pump casing and disposed on either side of the pump impeller 7.
  • the bulb casings 5 accommodate the pump motor or motors and the impeller blading control mechanism, and are attached to and supported within the pump casing 3 by a plurality of metal vanes 6 arranged around each bulb casing.
  • the vanes 6 both guide the flow of fluid through the duct, impart the necessary swirl to such fiow at the entrance to the impeller 7, and then restore the flow so that it leaves the downstream vanes at their original axial direction.
  • the whole hydraulic duct system comprising the impeller and bulb casings 3 and 5, respectively, is symmetrical with respect to a point on the pump axis XX.
  • the groups of guide vanes 6 around the bulb casings are positioned symmetrically with respect to an axis through point 0.
  • the guide vanes positions can be determined by adding a suitable rotation about the pump axis XX.
  • the pump impeller 7 is of the propeller type; a special feature of each blade being that its axis of symmetry is perpendicular to the axis of rotation XX and that these two axes intersect at the above designated point 0 as well hereinafter become more clear. Where the blade angle is adjustable, the axis of symmetry of a blade coincides with its swivelling axis.
  • the entire hydraulic duct system comprising the pump and bulb casings 3 and 5, respectively and guide vanes 6, is symmetrical with respect to a plane passing through the point 0 perpendicularly to the pump axis XX and indicated by the line II in FIG. 1 (the guide vanes can however, be determined by adding a suitable rotation about XX to this symmetry).
  • the guide vanes around each bulb casing 5 are symmetrically arranged about the pump axis XX.
  • impeller 7 is also of the propeller pump type; a special feature of each impeller blade being that its swivelling axis lies within its plane of symmetry, as will hereinafter become more clear.
  • the extreme positions at which the blades can 'be set by means of the control system are symmetrical with respect to the plane containing the line I-I.
  • FIG. 2 of the drawings shows in detailed outline the formation of the inlet and discharge orifices 1 embodied in the construction of FIG. 1.
  • the orifice 1 has the form of a symmetrical solid of revolution about the pump axis XX. Except where the orifice 1 joins the duct 4, its surface of revolution 8 diverges outwardly at a comparatively wide angle a, at least from the X-X axis.
  • the transition of the surface of revolution 8 section being taken a short I from this angle to its juncture with the duct 4 takes the form of a radius I", which is small compared to the diameter of duct 4 e.g. no more than one-quarter of this diameter.
  • This construction prevents breakaway when the flow is into the orifice i.e., from left to right as viewed in FIG. 2, and when the flow is in the opposite direction as indicated by the arrow in FIG. 2, such construction causes the w to break away cleanly so as to produce a discharging jet 9 of practically the same diameter as that of the adjoining end of'the duct 4.”
  • FIG. 3 of the drawings shows a modified form of inlet and discharge orifice .embodying the invention
  • the hydrojet duct sections 4 are connected to 'inturned flanges 1' forming the openings in the ships hull 2, and such openings are provided with bars 10 forming a-screen across them to. keep for: eign bodies out of thehydrojet.
  • the shape ofthe transition from the duct wall 4 to the exteriorof the hull plating 2, and the cross-sectional shape 0f bars .10, are such as to prevent breakaway in the inflow 1.e., fromtop to bottom as viewed in FIG. 3.
  • the screen bar cross-sections are made symmetrical with respect to their mean chord, with their widest part well towards the outside of the hull (see FIG. 3).
  • the hydraul c passages between adjacent bars and between the end bars and the transition from duct to hull plating will diverge sufliciently to ensure clean jet breakaway practically as soon as the flow passes the widest part of the bar crosssection.
  • FIG. 4 of the drawings shows the central portion of a hydraulic structure such as illustrated generally in FIG. 1, but constructed so that the flow reversal, and if necessary, fiow variatlons, are achieved by reversing the direction of rotatlon of the pump and by controlling its speed.
  • the reversible hydraulic apparatus of FIG. 4 includes a centrally located pump casing 3 containing an impeller 11 1ntermediate the symmetricalbulb casings 5 whlch are supported within such casing by the guide vanes 6.
  • the guide vanes 6 For the sake of clearness, only one guide vane is shown in detail on each side of the impeller, it being understood that the guide vanes 6 associated with each bulb casmg 5 are of similar construction.
  • the impeller pos1t10n is assumed to be such that the axis of symmetry, and possiblyialso the swiveling axis, of one of the impeller blades is perpendicular to the plane of the dlagrarn; the point 0 in FIG.
  • the numerals 16 and 17 indicate the inner and outer longitudinal edges, respectively, 'o the guide vanes; the inner lines 16 indicating the outline of the guide vane at the bulb casing 5 and the outer lines 17 indicating the outline of the guide vane at the inner wall of the bulb casing 3.
  • the numerals 18 and 19 indicate the inner and outer end edges, respectively, of the guide vanes, which end edges will act either as leading or trailing edges depending on the direction of flow of the fluid through the duct.
  • Each guide vane has the general shape of a fin; the portion thereof which is positioned farthest from the impeller 11, extending in the general direction of a plane radial to the X-X axis or one parallel thereto, and the portion thereof which is positioned nearest to the impeller 11, extending in a general direction inclined with respect to the XX axis.
  • each guide vane which is spaced farthest away from the impeller, approximately follows a radial plane extending out from the XX axis and perpendicular to the plane of the drawing, while the remaining portion of each vane adjacent to the impeller curves or inclines away from the radial plane passing through the XX axis and through the linear or major portion of the vane.
  • the guide vanes upstream of the impeller in addition to acting as distributor vanes, also impart to the fluid flow a swirl in the direction of pump rotation; the intensity of this swirl increasing from the pump cas ing to the bulb casing.
  • the guide vanes 6 are evenly spaced about the XX axis of the machine and act both as distributor vanes and flow straighteners (depending on whether they are upstream or downstream of the impeller in a given operation), while also forming a rigid support between the bulb casing 5 and the pump casing 3.
  • the line indicates the outline of a blade cross-section lying in a plane intersecting the axis of symmetry of the blade a short distance away from the impeller hub periphery.
  • the line 21 indicates the outline of a crosssection of the blade lying in a plane intersecting the axis of symmetry of the blade near the blade tip.
  • Both of the cross-sections shown are aerofoil sections, and the respective centres of symmetry thereof are the traces of their respective axes of symmetry O on the corresponding cross-sectional planes. It will be noted that unlike the more conventional type of aerofoil, which almost invariably features at least one sharp edge, the leading and trailing edges of these cross-sections are rounded-off.
  • the medians of these sections are in the general shape of a letter S with its point of infiexion coinciding with the centre of symmetry.
  • the angle of inclination of the blade profile medians with respect to a plane containing the line I-I and perpenddicular to the XX axis and intersecting it at the previously defined centre of symmetry 0 increases towards the impeller hub.
  • the impeller blades for such purpose are given a twisted shape to allow for the variable tangential fluid entrainment velocities along their leading and trailing edges.
  • FIG. 7 of the drawings is shown a view similar to FIG. 4 of a reversible axial pump constructed in accordance with the invention, wherein the flow is controlled, and reversed, by reversing the pitch of the impeller blades as required.
  • FIG. 4 the symmetrical bulb casings 5, the pump casing 3 and the impeller 11 of the construction of FIG. 7 are shown generally and only one of the guide vanes 6 provided on each side of the impeller is shown in detail.
  • the impeller is shown with one of its blades end-on, that is to say, with the blade swivelling axis perpendicular to the plane of the drawing and, as before, the trace of the intersection between axes XX and 1-1 is indicated by the predetermined point 0.
  • the line designated 22 indicates the outline of the blade at the impeller hub, and the line designated 23 indicates the profile of the blade at its tip.
  • the lines 24 and 25 designate the blade leading and trailing edges respectively.
  • the outlines of the guide vanes at their connection to the respective bulb casings 5 are indicated by the numerals 26, and the outlines of such vanes at their connection to the pump casing 3 are indicated by the numerals 27.
  • the leading and trailing end edges of the guide vanes, or -vice-versa, depending on the direction of flow, are indicated by the numerals 2S and 29.
  • FIG. 7 is in a radial plane, or in one parallel to the XX axis; the positions of the guide vanes shown in the drawings being such that the major portions of the vanes farthest away from the impeller are disposed from the bulb casings roughly on a radius running out from the XX axis and perpendicular to the plane of the drawings.
  • the shapes of the guide vanes in the construction of FIG. 7 are quite different from those described in the embodiment of FIG. 4 in that, basically, the ends of the guide vanes nearest to the im-. peller are more steeply inclined in the direction of impeller rotation near the pump casing 3 than they are at the bulb casing 5. As is illustrated in FIG.
  • the inclination of the guide vane near the bulb casing may even run contrary to the direction of rotation of the impeller. It will also be noted in FIG. 7 that the angle of guide vane inclination varies continuously from the impeller periphery towards the hub, in order to impart a swirl in the direction of impeller rotation to the water when the guide vane is acting as a distributor vane. This swirl is most pronounced in the flow nearest the periphery, but may be reduced to zero or reversed near the hub.
  • FIGS. 8 and 9 of the drawings show cross-sectional outlines of the impeller blade in planes perpendicular to the blade swivelling axis.
  • the outline in FIG. 8 designated 30 is the outline of the blade cross-section taken perpendicularly to and intersecting the blade swivelling axis at a point near the impeller hub.
  • the outline in FIG. 9 designated 31 is the outline of the blade cross-section which lies in a plane parallel to the above, but intersects the blade swivelling axis near the blade tip.
  • the lines J] and J'I in these two figures are the traces of the plane of symmetry of the blade, in the above mentioned cross-sectional planes and are therefore parallel. They thus represent the axes of symmetry and the mean chords of the cross-sections 30 and 31. Contrary to the blades in the embodiment of FIG. 4, the blades in the construction of FIG. 7 are rounded-off at one end and sharp at the other; the former acting as the leading edge and the latter acting as the trailing edge, irrespective of the direction of flow. It should also be noted that the thickness chord ratio of the profiles is substantially constant, from the centre to the periphery of the blades.
  • the direction of the flow produced by a propeller pump can for example be reversed without reversing the direction of pump rotation, by swivelling each impeller blade so that the angles of inclination with respect to the median plane of all of its profiles are symmetrically opposite to those angles present when the blades are in their original positions. Continuous thrust reversals can be achieved in this way, as the angle of blade inclination will decrease progressively before changing its sign.
  • The'absence of blade twist in the blades employed in the construction of FIG. 7, also requires the type of flow straightening and distribution vanes 6 described above, in order that suitable angles of incidence may be obtained on the impeller blades and guide vanes in both flow directions.
  • reversible flow axial pumps embodying the invention are not restricted to hydrojets. These pumps can be used for any application requiring a reversible flow. It will also be understood that the special features described herein, especially where referring to symmetry of form, arrangement of impeller blades and guide vanes, and their mutual adaptation, can also be applied to axial or pump turbines for instance with a view to harnessing hydraulic power under reversible heads. It is of course possible, with respect to reversible flow axial pumps embodying the invention to adjust the pump speed, and/or the blading angles, to obtain, at all times, the optimum operating conditions.
  • Reversible hydraulic apparatus comprising an elongated dust having at its ends two orifices facing outwardly in opposite directions and having end portions of such similar construction that each such duct end portion is capable of functioning as an inlet and as an outlet for fluid passing therethrough, both of said duct end portions being constructed to insure a total absence of fluid breakaway when used as an inlet, and when used as an outlet to cause the fluid to break away cleanly and discharge in the form of a jet, a hydraulic machine operable to cause reversible hydraulic flows through said orifice and constituted of a pump or turbine centrally located within said duct and having rotor vane blades the profiles of which are symmetrical with respect to a plane defined by the cords of all the profile cross sections, this plane of symmetry containing the blade rotating axis, a pair of streamlined casing symmetrically disposed on both sides of said plane with said hydraulic machine therebetween, said casings extending longitudinally centrally of said duct between said orifices with their longitudinal central axes coinciding
  • each duct end portion is composed of a frusto-conically shaped wall diverging outwardly at an angle greater than 20, said wall merging from such'angle at its inner reduced end into a wall portion defining-a diverging opening curved through va given radius.
  • Reversible hydraulic apparatus comprising an elon-' gated duct having at its ends two orifices facing outwardly in opposite directions and having end portions of suchsimilar construction so that each such duct end: portion is capable of functioning as an inlet and as an outlet for fluid passing therethrough, a hydraulic machine operable to cause reversible hydraulic flows through said orifices and constituted by a pump or turbine centrally located within said duct and having a hub and rotor blading the profiles of which are symmetrical with respect to a plane defined by the chords of all the profile cross sections,.this plane of symmetry containing the blade rotating axis, said rotor blading being adjustable and constructed toreverse the direction of fluid flow while maintaining one direction of rotation, a pair of streamlined casings symmetrically disposed on both sides of said rotational axis with said hydraulic machine therebetween, said casings extending longitudinally centrally of said duct between said ori fices with their longitudinal central axis coinciding with the longitudinal central axi
  • Reversible hydraulic apparatus such as defined in claim 3, in which the inner end portions of said vanes are inclined at a greater angle near said duct wall than near said casing so that the swirl in the fluid is more pronounced nearest the periphery of said duct passage.
  • Reversible hydraulic apparatus comprising an elongated duct having at its ends two orifices facing outwardly in opposite directions and having end portions of such similar construction so that each such duct end portion is capable of functioning as an inlet and as an outlet for fluid passing therethrough, a hydraulic machine operable to cause reversible hydraulic flows through said orifices and constituted of a pump or turbine centrally located within said duct and having a hub and adjustable rotor vane blades constructed to reverse the direction of fluid flow while maintaining one direction of rotation, said vane blades being symmetrical relative to a straight plane at the midpoint of the axial extremities of the rotor and perpendicular to and intersecting the longitudinal central axis of said elongated duct, said blades having a rounded leading edge and a relatively sharp trailing edge and the profile of each blade being symmetrical with respect to a straight plane defined by the chords of the profile of all sections of the blade and containing the blade rotating axis, a pair of streamlined casings symmetrically
  • Reversible hydraulic apparatus such as defined in claim 5, in which the inclination of the inner end portions of said vanes near said casing is counter to the direction of rotor rotation.
  • Reversible hydraulic apparatus such as defined in claim 5, in which said blading is at the angular position of +13 for one direction of flow, and at the angular position of B for the other direction of flow, the construction of said blading being such that the thickness chord ratio of the profiles is substantially constant from the center to the periphery of said blading.
  • Reversible hydraulic apparatus comprising an elongated duct having at its ends two orifices facing outwardly in opposite directions and having end portions of such similar construction so that each such duct end portion is capable of functioning as an inlet and as an outlet for fluid passing therethrough, both of said duct end portions being constructed to insure a total absence of fluid breakaway when used as an inlet, and when used as an outlet to cause the fluid to break away cleanly and discharge in the form of a jet, each of said orifices having a screen of bars across the opening thereof, said bars having cross sections symmetrical with respect to a mean chord extending parallelly to the central axis of the associated duct end portion and of tear drop shape with the widest part of said cross-section at the outer end of said associated duct end portion, and the surface portions of the outer end of said associated duct end portion in opposed relation to the outer sides of the end bars in said screen having configurations comparable of the configurations of the latter, whereby the hydraulic passages formed between adjacent bars and between the end bars and said duct

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US577089A 1963-01-19 1966-09-02 Reversible hydraulic apparatus Expired - Lifetime US3406632A (en)

Applications Claiming Priority (1)

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FR4526A FR1353655A (fr) 1963-01-19 1963-01-19 Hydroréacteur

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US732577A Expired - Lifetime US3464357A (en) 1963-01-19 1968-05-28 Reversible hydraulic apparatus

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US (2) US3406632A (de)
DE (1) DE1528824C3 (de)
DK (1) DK113480B (de)
ES (1) ES295461A1 (de)
FR (1) FR1353655A (de)
GB (1) GB1047891A (de)
NL (1) NL6400294A (de)
NO (1) NO121823B (de)
SE (1) SE321417B (de)

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CN109798215A (zh) * 2019-03-27 2019-05-24 西北农林科技大学 一种新型超低比转速水泵水轮机

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CN109798215B (zh) * 2019-03-27 2020-05-29 西北农林科技大学 一种新型超低比转速水泵水轮机

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ES295461A1 (es) 1964-07-16
FR1353655A (fr) 1964-02-28
DK113480B (da) 1969-03-24
NL6400294A (de) 1964-07-20
DE1528824C3 (de) 1975-03-20
DE1528824B2 (de) 1974-08-08
US3464357A (en) 1969-09-02
SE321417B (de) 1970-03-02
NO121823B (de) 1971-04-13
DE1528824A1 (de) 1969-10-30
GB1047891A (en) 1966-11-09

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