AU627043B2

AU627043B2 - Pump with peripheral driving jets

Info

Publication number: AU627043B2
Application number: AU57819/90A
Authority: AU
Inventors: John Stanley Melbourne
Original assignee: Individual
Current assignee: Individual
Priority date: 1989-06-29
Filing date: 1990-06-25
Publication date: 1992-08-13
Anticipated expiration: 2010-06-25
Also published as: AU5781990A

Description

I

AUSTRALIA

Patents Act 62?04 COMPLETE SPECIFICATION

(ORIGINAL)

Class Int. Class Application Number: Lodged: .9 *9 9 9 9

S@

9 9

S.

9** 9.

9 9 9.9 C 99 9. 9 99 9 9 99.9 Complete Specification Lodged: Accepted: Published: Priority Related Art: APPLICANT'S REF.:. CAP of PJ4999 Name(s) of Applicant(s): Address(es) of Applicant(s): JOHN STA~NL 1 EY DIEE3JEJRNE 2/4 13 Dorset Road, Boronia, Victoria 3155, Australia 9 99 .9 9 .99 9 9. 9 9 9 99 Actual Inventor(s).

Address for Service is: PHILLIPS, ORMONDE AND FITZPATRICK Patent and Trade Mark Attorneys 367 Collins Street Melbourne, Australia, 3000 Complete Specification for t~ie invention entitled: Nl- WITH PERIPHERAL DRIVING JETS" The following statement i,1 a full description of this invention, including the best method of performing it known to lo4* PUMP WITH PERIPHERAL DRIVING JETS This invention relates to an improved pump, enabling pumping of flowable materials by the action of peripheral driving jets.

According to the invention, there is provided a pump device, suitable for pumping a material comprising particulate solids, a liquid, a paste or particulate solids dispersed in a liquid or paste, for contacting such material with a reactant liquid or for mixing such material with a second liquid, the device comprising an elongate tubular body which defines a through bore extending between inlet and outlet ends thereof; an annular chamber which is defined intermediate said inlet and outlet ends and extends substantially concentrically around the bore; an inlet port to the chamber adapted to be connected to a source of pressurised liquid for supply of said pressurised liquid to the chamber; and a plurality S'"of circumferentially spaced passages providing communication between the chamber and the bore, each 20 passage having an opening to the bore which opening faces towards the outlet end such that pressurised liquid supplied to the chamber issues from said outlet end via said passages; each said passage having its said opening *at a radially extending shoulder which faces towards said 25 outlet end of the bore, with the bore converging from an outer circumference of the shoulder over a relatively short portion of ihe length of the bore, to a downstream bore portion which is of :ubstantially constant cross-section and with the bore being of substantially the same constant cross-section from said inlet end to said shoulder; the device being such that, on connection of said inlet port to said pressurised liquid source and with said inlet end in (ommunication with a source of a said material, the pressuiised fluid discharged into the bore via said passages generates a reduction in pressure in the bore upstream of said passage openings such that said material is drawn through said bore and thereby pumped .Ik from the outlet end of the bore.

The device has some similarity to pneumatic devices 0 2 2757L l i

I

2 of the type referred to as an air mover or air pump.

However, unlike st. h devices, the device of the invention is adapted for use in pumping or transporting a solid in particulate form, a liquid, or particulate solids in a liquid for purposes such as indicated above.

Alternatively, the device of the invention can be used to provide mixing or reaction between pressurised liquid and such solids or liquid, or reactiu,, between such liquid and particulate material of a fluid comprising particulate solids entrained in the liquid. Particulate solids able to be pumped or transported include food products such as meat pieces, beans and grain, and mineral products such as coal, ores and concentrates.

Efficient pumping action is enabled by the device of the invention as a consequence of the passages having their openings at a radially extending shoulder which .faces towards the outlet end of the bore. From the outer circumference of the shoulder, the bore converges over a relatively short portion of its axial extent to the S 20 downstream bore portion which is of substantially the same constant cross-section. From the inlet end to the shoulder, the bore is of the same substantially constant cross-section along an upstream bore portion.

It is highly desirable, in order for the device to be able to function most efficiently as a pumnp, for the diameter of the bore upstream of the passage openings to be substantially equal to that of the bore downstream of 1 those openings.

It also is highly desirable, for slich efficieat functioning, for the length of the bore downstream of the passage openings to be related to the angle of inclination of the passages to the bore axis. The passages are required to be inclined so that jets of pressurised liquid issuing therefrom converge upstream from the outlet end Such convergence preferably is at a location of not less than half the distance from the openings to the outlet end. The location of convergence of the jets most preferably is about two-thirds of the way along that fi distance from the openings, although this location can be 0-3 -i 2757L 4-

L

varied readily by minus 10 percent and plus 20 percent of that spacing, such as from mini- 5 percent to plus percent. The length of the bore downstream of the openings preferably is such that the passages can be inclined to the axis of the bore at an angle of from degrees to 20 degrees. Such inclination may for example be from 12.5 degrees to 17.5 degrees and most preferably is about 15 degrees.

n 3a 2757L i i I (i: i.; I "iS 1 I jlu-~ I' .I L It further is highly desirable that the cross-sectional area of the downstream bore portion does not exceed the aggregate cross-sectional area of the passages by a ratio greater than 25:1. However, that ratio preferably is not greater than 15:1, and more preferably is less than 10:1. A ratio of 5:1 is found to achieve an excellent pumping action, although the ratio can be still lower, such as 1:1 or evon 1:2. A ratio of 5:1 to 1:1 is most preferred.

Even at an area ratio of 25:1 as specified above, the device differs significantly from similar air pump or air mover devices. That is, such ratios necessitate a :relatively high aggregate cross--sectional area for the passages. The passages therefore typically are closely spaced around the bore, preferably with spacing between successive passages being relatively small compared wil-h the diameter of the passages.

Correspondingly, it is desirable that the crosssectional area of the chamber perpendicular to the bore o* 20 axis be large relative to the cross-sectional area of the downstream bore portion. However, the ratio of that .999 cross-sectional area of the chamber to the aggregate cross-sectional area of the passages most preferably is less than the ratio of the cross-sectional area of the downstream portion of the bore to that aggregate area of the passages. Most preferably the cross-section of the inlet port is large relative to the cross-sectional area of the chamber parallel to the bore axis.

It is highly preferred that the inlet port leads tangentially into the chamber. This generates an annular flow of pressurised liquid within the chamber, and facilitates flow of the liquid into and through the passages so as to issue into the bore as jets.

In order that the invention may more readily be understood, reference is directed to the accompanying drawings, in which: Figure 1 is a longitudinal sectional view through a fluid pump according to the invention; and 39 Figure 2 is a sectional view of the pump, taken on 5379L i r- 1 i-A line II-II of Figure 1.

With reference to the drawings, the device has :n elongate tubular body 10 which defines a through bore 12 extending between the inlet and outlet ends of body Upstream and downstream portions of bore 12 are defined by respective annular pipe sections 18,20, between which an annular chamber 22 is defined. Chamber 22 is enclosed by a flange 24 welded to pipe section 18, an annular sleeve 26 having a hub portion 26a received on pipe section 20 and welded thereto, and an inner annular sleeve which defines an intermediate portion of bore 12 .between pipe sections 18,20. An "O-ring" seal 29a is provided between flange 24 and outer sleeve 25, while a similar seal 29b is provided between pipe section 18 and the adjacent end of inner sleeve 28 and a further seal 29c is provided between the other end of sleeve 28 and a radially inner flange 26h of sleeve 26.

Adjacent pipe section 20, the inner circumference of inner sleeve 28 is stepped to provide an annular shoulder 20 30 which faces towards outlet end 16 of body 10. From the "outer periphery of P' 'der 30, that circumference of \sleeve 28 tapers fru-i nically inwardly so as to merge via the inner circumference of flange 29c with the portion of bore 12 defined in pipe section Around the circumference of shoulder 30, inner sleeve 28 is provided with a plurality of closely spaced passages 32, each of which provides communication between chamber 22 and bore 12. Also, outer sleeve 26 defines an inlet port 34 by which body 10 is connectible to a source of high pressure liquid. Port 34 communicates with chamber 22, such that high pressure liquid supplied to port 34 flows into chamber 22 and issues from the latter into bore 12, via passages 32, as high pressure jets.

Port 34 most preferably is substantially tangential with respect to chamber 22 so that liquid supplied to chamber 22 is caused to flow around that chamber.

eassages 32 open at shoulder 30 and are inclined with respect to axis A of bore 12 such that the jets 39 issuing from passages 32 converge at a location B along 5379L

I

axis A which is about two-thirds of the way along pipe section 20 towards end 16 of body 10. The inclination of passages 32 with respect to axis A is from 100 to preferably from 12.50 to 17.50 such as at about 150°.

The cross section of bore 12 in pipe section 18 is required to be substantially the same as that in pipe section 20, as shown.

The cross-section of bore 12 in pipe section should not exceed the aggregate cross-sectional area of passages 32 by a ratio greater than 25:1. The ratio can be substantially less than 25:1 as detailed above, such as about 5:1. Passages 32, which most preferably are of circular cross-section, preferably have a transverse dimension which is large relative to the radial extent of shoulder 30. Also, to ensure such ratio of not greater than 25:1, successive passages 32 preferably are relatively closely spaced circumferentially around bore 12, with the spacing between successive passages 32 most preferably being less than such transverse dimension.

20 For a pump in which pipe section 20 is about 2 I: inches in diameter, such as from 1.75 to 2.25 inches, there may be about 34 passages 32 of about 3/16 inch diameter. For a pump in which section 20 is about 4 inches in diameter, such as from about 3.5 to 4.5 inches, 25 there may be about 40 passages 32 of about 5/16 inch diameter. Similarly, for a diameter of about 6 inches for section 20, such as about 5.5 to 6.5 inches, there may be S:o: about 50 passages 32 of about 5/8 inch diameter.

The cross-sectional area of chamber 22 perpendicular to ax4.s A preferably is large relative to the cross-sectional area of bore 12 in pipe section 20. That area of chamber 22 most preferably is at least 80% of, and may exceed, that area of bore 12. The ratio of the cross-sec+ional area of chamber 22 perpendicular to axis A to the aggregate cross-sectional area of passages 32 most preferably is less than the ratio of the cross-sectional area of bore 12 in pipe section 20 to that aggregate area 6 S) ,757L y

IA

of passages 32.

Port 34 preferably has a cross-section which is large relative to the transverse cross-sectional area of chamber 22 parallel to axis A. That area of port 34 preferably is at least 80% of, and may exceed, that transverse section of chamber 22.

In use of the pump of Figures 1 and 2, high pressure liquid is supplied to port 34 so as to fill chamber 22 and issue from passages 32 as high pressure jets converging at location B on axis A. Those jets generate a reduction in pressure in bore 20 upstream of the passages such that the device can be used to transport solids in particulate form, a second liquid or particulate material entrained in o. a second liquid with which inlet end 14 is in communication such that the solids or liquid is drawn ag oalong bore 12 for discharge from end 16 with the liquid of the high pressure jets. The device therefore is able to pump or transport the particulate solids or a second liquid to a required location, such as by a hose fitted to 20 end 16 of the device. However, within the device, the liquids or the solids and pressurised liquid can be caused to nmi. intimately, while the liquid supplied to port 34 may be such as to react with the second liquid or with the solids.

Finally, it is to be understood that various alterations, modifications and/or additions may be introduced into the constructions and arrangements of parts previously described without departing from the spirit or ambit of the invention.

i39 39 I 5379L &MM_

Claims

1. A pump device, suitable for pumping a material comprising particulate solids, a liquid, a paste or particulate solids dispersed in a liquid or paste, for contacting such material with a reactant liquid or for mixing such naterial with a second liquid, the device comprising an elongate tubular body which defines a through bore extending between inlet: and outlet ends thereof; an annular chamber which, is defined intermediate said inlet and outlet ends and extends substantially concentrically around the bore; an inlet port to the chamber adapted to be connected to a souirce of pressurised liquid for supply of said pressurised liquid to the chamber; and a plurality of circumferentially spaced passages providing communication between the chamber and the bore, each passage having an opening to the bore which opening faces towards the outlet end such that pressurised liquid supplied to the chamber issues from said outlet end via said passages; each said passage having its said 20 opening at a radially extending shoulder which faces towards said outlet end of the bore, with the bore converging from an outer circumference of the shoulder over a relatively short portion of the length of the bore, to a downstream bore portion which is of substantially constant cross-section and with the bore being of substantially the same constant cross-section from said inlet end to said shoulder; the device being such that, on connection of said inlet port to said pressurised liquid source and with said inlet end in communication with a source of a said material, the pressurised fluid discharged into the bore via said passages generates a reduction in pressure in the bore upstream of said passage openings such that said material is drawn through said bore and thereby pumped from the outlet end of the bore.

2. A device according to claim 1, wherein said chamber is defined by said elongate body.

3. A device according to claim 1, wherein said chamber is defined at least in part by a fitting extending around and secured to said elongate body. zlZ j7N (i cc-, \r 9/757L3 'iMr 8 *1 l r 2 s- r srjr u n D r u r (I i

4. A, device according to any one of claims 1 to 3, wherein upstream of the passage openings the bore has a cross-section substantially equal to its cross-section downstream of those openings.

5. A device according to any one of claims 1 to 4, wherein the passages are inclined to the bore axis such that jets of pressurised liquid issuing therefrom converge at a location upstream from the outlet end.

6. A device according to claim 5, wherein said location is spaced from the openings by not less than half the distance from the openings to the outlet end.

7. A device according to claim 6, wherein said location is spaced from said openings by from 57% to 87% of said distance.

8. A device according to claim 6, wherein said location is spaced from said openings by from 62% to 82% of said distance.

9. A device according to any one of claims 1 to 8, wherein said passages are inclined to the bore axis at an 20 angle of from 10 to 200

10. A device according to claim 9, wherein said angle is from 12.5 to 17.50.

11. A device according to any one of claims 1 to wherein the bore has a cross-sectional area downstream of said openings which does not exceed the aggregate cross-sectional area of said passages by a ratio of more than 25:1.

12. A device according to claim 11, wherein said ratio is not greater than 15:1.

13. A device according to claim 11, wherein said ratio is less than 10:1.

14. A device according to claim 11, wherin said ratir is from 5:1 to 1:1. A device according to any one of claims 1 to 14, wherein the spacing between successive passages is small relative to the diameter of the passages.

16. A device according to any one of claims 1 to wherein the chamber has a cross-sectional area perpendicular to the bore axis which is large relative to i2k.' c -2757L zp 9 L I r the cross-sectional area of the bore downstream of said openings.

17. A device according to claim 16, wherein the ratio of said cross-sectional area of the chamber to the aggregate cross-sectional area of the passages is less than the ratio of the cross-sectional area of the bore downstream' of the openings to said aggregate area.

18. A device according to any one of claims 15 to 17, wherein said inlet port leads tangentially into said chamber.

19. A device according to claim 1, substantially as herein described with reference to the accompanying drawings. DATED: 10 April 1992 PHILLIPS ORMONDE FITZPATRICK Attorneys for: JOHN STANLEY MELBOURNE q_ *e 4 *2 e* e 10 2757L