WO1998048172A1 - Ameliorations de pompes a helices - Google Patents

Ameliorations de pompes a helices Download PDF

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Publication number
WO1998048172A1
WO1998048172A1 PCT/AU1998/000264 AU9800264W WO9848172A1 WO 1998048172 A1 WO1998048172 A1 WO 1998048172A1 AU 9800264 W AU9800264 W AU 9800264W WO 9848172 A1 WO9848172 A1 WO 9848172A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
impeller
drive shaft
hub
blades
Prior art date
Application number
PCT/AU1998/000264
Other languages
English (en)
Inventor
John Eastman Barnes
Original Assignee
John Eastman Barnes
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 John Eastman Barnes filed Critical John Eastman Barnes
Priority to AU69112/98A priority Critical patent/AU722618B2/en
Priority to US09/403,246 priority patent/US6213740B1/en
Priority to EP98914704A priority patent/EP0993554A4/fr
Publication of WO1998048172A1 publication Critical patent/WO1998048172A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C5/00—Rotary-piston machines or pumps with the working-chamber walls at least partly resiliently deformable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/02—Glass

Definitions

  • This invention relates to improvements to rotary pumps and more specifically to pumps that incorporate rotating flexible impellers for their pumping action.
  • rotary pumps have a housing that allows access to an impeller via an end cover.
  • the impeller is driven by a drive shaft that causes water to be drawn through an inlet at low pressure and expelled through an outlet at higher pressure.
  • the invention resides in a pump including a flexible impeller and a housing having a pump end cover, the pump end cover comprising: a transparent safety cover able to be attached to the housing; a transparent heat resistant insert able to contact the impeller; and a spacing means to space the transparent heat resistant insert from the transparent safety cover.
  • the transparent heat resistant insert may be made from any suitable material and may be of any suitable shape or size.
  • the transparent heat resistant insert is made from borosilicate glass.
  • the transparent safety cover may be made from any suitable material and may be of any suitable shape or size.
  • the transparent safety cover is made from an acrylic plastics such as perspex or a polycarbonate plastics such as lexan.
  • the spacing means may be made of any suitable form.
  • the spacing means may be a mounting ring.
  • the spacing means may hold the transparent insert at a fixed distance from the transparent safety cover.
  • the spacing means has a positioning means that allows the transparent heat resistant insert to position itself against the impeller.
  • the positioning means may be a substantially flexible "O" ring.
  • the "O" ring may be hollow.
  • the pump end cover may be attached to the housing by mounting means.
  • the mounting means may include a mounting fastener that is able to extend through the pump end cover, and a retaining sleeve to prevent unwanted removal of the mounting screw from the pump end cover.
  • the mounting fastener may be a standard fastener such as an alien bolt or Phillips head screw.
  • the retaining sleeve may be formed from any suitable tubular flexible material.
  • the retaining sleeve is made of natural or synthetic rubber.
  • the impeller may include a hub that is able to be attached to a drive shaft, and a plurality of flexible blades extending outwardly from the hub, wherein the blades are removable from the hub.
  • the blades may be inserted or removed from the hub by moving the blades in an axial direction relative to the hub.
  • the hub may have a plurality of equally spaced profiled slots into which corresponding end portions of the blades can be inserted.
  • Each blade may be substantially symmetrical such that either end portions of the blade can be inserted into a profiled slot.
  • the blades and hub may be made from different materials having different wear properties so that both the hub and the blades operate more effectively.
  • a seal may be located on at least one end of the hub to establish substantially water tight zones between respective blades.
  • the seal is an "O" ring.
  • the impeller may also include a threaded hole that is in communication with a drive boss such that a threaded shank can be rotated within the threaded hole to remove the drive boss from the drive shaft.
  • the shank may be of any suitable form.
  • the threaded shank forms part of a bolt.
  • the drive shaft may be attached to the impeller by a lost motion device that allows at least limited relative rotation between the drive shaft and the impeller.
  • the lost motion device may be of any suitable form.
  • the lost motion device includes at least one impeller key mounted to the impeller and at least one drive shaft key mounted to the drive shaft such that upon rotation of the drive shaft the keys contact each other to rotate the impeller.
  • the lost motion device comprises a hollow ring mountable to the impeller having three equally spaced impeller keys formed on an inner circumference of the ring, and a collar mountable to the drive shaft having three equally spaced drive shaft keys formed on an outer circumference of the collar.
  • a pressure sensing nipple may be used to determine the pressure within the pump and also fasten a cam of the pump. After much trial and experimentation it has been found that placement of the nipple through the cam will give a value of pressure proportional to the outlet pressure of the pump.
  • a temperature warning device may be attached to the transparent heat resistant insert to monitor the temperature of the pump.
  • the temperature warning device may be attached adjacent the centre of the transparent heat resistant insert as heat generated by friction of the impeller rubbing against the pump will at be at its most intense at the centre of the transparent insert.
  • the invention resides in a pump end cover including: a transparent safety cover able to be attached to a pump housing; a transparent heat resistant insert able to contact the impeller; and a spacing means to space the transparent heat resistant insert from the transparent safety cover.
  • the pump end cover may have the same features as described previously,
  • the invention resides in an the impeller including: a hub able to be attached to a drive shaft and a plurality of flexible blades extending outwardly from the hub; wherein the blades are removable from the hub.
  • the impeller may have the same features as described previously.
  • the invention resides in a removable blade for a flexible impeller including an end portion that is able to be inserted within a profiled slot of a hub of the impeller.
  • the blade may have the same features as described previously.
  • the invention resides in an impeller including a threaded aperture that is in communication with a drive boss of an impeller such that a threaded shank can be rotated within the threaded hole to move the shank inwardly to remove an impeller drive boss from a drive shaft.
  • the impeller may have the same features as described previously.
  • the invention resides in a lost motion device for connecting a drive shaft to an impeller, the lost motion device allowing reverse rotation of the drive shaft of less than 360 degrees without rotation of the impeller.
  • the lost motion device may have the same features as described previously.
  • the invention resides in a pressure sensing nipple that is used to determine the pressure within the pump and also to fasten a cam of the pump.
  • the pressure sensing nipple may have the same features as described previously.
  • the invention resides in a temperature warning device for a pump, the temperature warning device attached to an end cover to monitor the temperature of the pump.
  • the end cover may be constructed from any suitable materials such as metal. Preferably the end cover is constructed similar to that described previously.
  • the temperature warning device may be attached adjacent the centre of the end cover.
  • FIG. 1 is a perspective view of a marine engine cooling pump according to one embodiment of the invention.
  • Figure 2 is a cross sectional view of the marine engine cooling pump of Figure 1.
  • Figure 3 is another cross sectional view of a marine engine cooling pump according to another embodiment of the invention.
  • Figure 4 is a partial sectional view of an impeller attached to a pump drive shaft.
  • Figure 5 is a is further partial sectional view of an impeller attached to a pump drive shaft.
  • Figure 6 is an end elevation of a marine engine cooling pump according to another embodiment of the invention.
  • Figure 7 is a perspective view of a impeller used in the marine cooling pump shown in Figure 6.
  • Figure 8 is a further end elevation of a marine engine cooling pump according to another embodiment of the invention.
  • FIG. 1 shows a pump 10 having a flexible impeller 20 connected to a drive shaft 30 and a housing 40 having a transparent pump end cover 50.
  • a pump 10 having a flexible impeller 20 connected to a drive shaft 30 and a housing 40 having a transparent pump end cover 50.
  • FIG 2 is a cross sectional view of the pump 10 which shows the impeller 20 located in the pump housing 40 to which is attached a transparent pump end cover 50 consisting of a borosilicate glass insert 51 , glass insert mounting ring 53 and transparent safety cover 52.
  • a well known problem with existing pump end covers manufactured out of metal is the wear experienced on the inside face of the pump end cover as a result of the continual rubbing action of the flexible impeller as the end cover acts as a retaining, sealing plate for the impeller.
  • the use of a heat resistant and hardened borosilicate glass greatly reduces wear and the possibility of glass failure due to thermal stress from heat buildup caused by friction between the impeller and adjacent surface of glass insert.
  • the transparent pump end cover 50 can be further strengthened with the addition of a transparent safety cover 52 which also serves as a containment barrier in the event of failure of the glass insert 51.
  • a transparent safety cover 52 is a most desirable feature when pumping dangerous or corrosive fluids or in marine engine applications where the pump may be mounted below the waterline of the vessel and any failure of the glass insert could result in flooding of the vessel.
  • FIG. 2 Yet another feature of the transparent pump end cover 50 shown in Figure 2, is the incorporation of a hollow chamber 54 filled with air located between the glass insert 51 and the transparent safety cover 52 which greatly reduces the risk of heat distortion or failure of the transparent safety cover 52.
  • the hollow chamber 54 filled with air acts as an insulation barrier where any heat buildup in the glass insert 51 is not directly transferred to the transparent safety cover 52 which is more susceptible to heat distortion than the glass insert 51.
  • any of these variables or a combination of them can result in the clearance between the inside surface of the glass insert 51 and the impeller 20 being too tight thereby building up heat which can result in premature failure of the glass insert 51 or failure of the impeller 20 or both.
  • Figure 3 is an arrangement that addresses these problems by use of a glass insert 51 that is allowed to automatically position itself in relation to the adjacent face on impeller 20.
  • transparent pump end cover 50 is designed to accommodate a glass insert 51 and a circular hollow flexible "O" ring seal 55 bonded between the outside surface of the glass insert 51 and the inside surface of the mounting ring 53 thereby providing a water proof seal between the mounting ring 53 and the glass insert 51.
  • the flexible seal 55 can be manufactured out of a suitable material such as high temperature silicone rubber which has excellent resilience and memory properties so that it can perform the functions of both a seal and resilient spring.
  • glass insert 51 can position itself against an outer face of the impeller 20 and compensate for the variables previously described.
  • Figure 3 also includes flat sections 56 on the outer edge of glass insert 51 and the inside of mounting ring 53 to prevent the glass insert 51 from rotating.
  • FIGS. 2 and 3 show mounting means 60 where mounting screws 61 are held captive by a flexible retaining sleeve 62 located in hole of the mounting ring 53.
  • This simple and effective arrangement provides mounting means 60 where the screws 61 can initially be rotated by hand to start the screw into a threaded hole of the pump 10 and finally be tightened securely with a suitable tool such as an hexagonal key or spanner or screwdriver depending on the type of screw head.
  • Figure 2 and 3 also show a flexible plug 70 installed in recess 71 of the flexible impeller that is designed to reduce the ingress of fluid and build up of salt or corrosion between the drive shaft 30 and an impeller drive boss 21.
  • FIG 4 shows a portion of a cross section of an impeller drive boss 21 assembled in the normal position on drive shaft 30.
  • the impeller drive boss 21 has been modified to include a threaded hole 80 at the impeller outer end that can accept a threaded bolt 81 for removal of the impeller 20 from the drive shaft 30 as shown in Figure 5.
  • Figure 5 shows the same portion of an impeller cross section where the threaded bolt 81 has been screwed into the impeller drive boss 21 thus extracting the complete impeller 20 from the drive shaft 30 to a position where the impeller can be removed by hand.
  • Figure 6 shows an end elevation of an impeller 20 that consists of a solid hub 90 with a series of profiled slots 92 positioned around longitudinal axis of the hub 90 and shaped to accept a number of matching flexible impeller blades 91.
  • the impeller blades 91 will remain in place in profiled slots 92 thus resisting centrifugal force or pump cam impeller blade distortion forces during rotation and being restrained longitudinally by the transparent pump end cover 50 when the pump 10 is installed in a pump housing.
  • the normal failure mode of a conventional flexible impeller occurs when the impeller blades tear away from the impeller hub in the vicinity of the base of the impeller blades and is caused by the stress involved as the individual blades pass over the pump cam.
  • removable replacement blades 91 can have appeal to the end user and is a cost effective solution because higher performance materials can be used for impeller blade construction without the requirement to manufacture the remainder of the impeller from the same material.
  • a flexible heat resistant "O" ring 93 is set into the impeller hub 90 to effectively seal each zone 100 located between adjacent impeller blades 91.
  • a side elevation of this arrangement is also shown in Figure 3, where "O" ring 93 is set into a groove in hardened impeller boss.
  • this engine driven cooling pump 10 has a normal clockwise rotation therefore the blades 91 will normally be displaced to the left as they pass over a pump cam 110 and this normal direction of rotation is recommended by impeller manufacturers whilst installation of an impeller 20 is in progress. This installation procedure is designed to minimize stress on the impeller blades 91 during the subsequent start up of the engine. It should also be noted that some small electric pumps will fail to run if the impeller is inserted with incorrect impeller rotation.
  • FIG 8 shows an impeller end elevation 8 where the impeller 20 includes a hub 90 having outwardly extending circumferentially spaced keys 120 and the drive shaft consists of a collar 130 having outwardly extending, circumferentially spaced keys 131 arranged in such a manner to form a lost motion device that enables the drive shaft 30 to rotate approximately 100 degrees in the opposite direction from the normal direction of rotation without a corresponding movement of the impeller 20.
  • the impeller remains in the normal rotational position whilst the drive shaft 30 and collar 130 moves in the opposite direction thereby greatly relieving subsequent stress on the impeller blades 91 and therefore prolonging impeller life.
  • This type of impeller design has the added advantage of being relatively easy to remove because the lost motion device is by design a relatively loose fit between hub 90 and collar 130.
  • FIG 3 shows yet another simple improvement in the ability to remotely monitor pump performance as a conventional cam screw is replaced with a hollow nipple 140 that acts both as a cam retaining screw and a pressure sensing line attachment fitting.
  • a direct reading pressure gauge or pressure transmitter or pressure switch or combination of each could be directly mounted to the cam screw attachment point without the need of additional hardware or plumbing.
  • a pressure switch (not shown) could be setup to automatically shut down the engine thus preventing the possibility of impeller or engine damage from a blocked, restricted or broken pump inlet line.
  • the connection of a suitable warning device via a pressure switch would provide an early warning of potential impeller damage should the pump inlet become blocked by some foreign object such as a plastic bag or seaweed.
  • Another technique in the monitoring of flow through a flexible impeller pump is to manually feel the temperature at the centre area of the transparent pump end cover 50.
  • a reduction or cessation of flow rapidly increases the temperature of the transparent pump end cover 50 and this temperature increase can be monitored by means of a temperature switch or similar device attached to the outside surface of a typical metal end cover.
  • the temperature monitoring device consists of a thermistor 150 bonded to the surface of the glass insert

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe (10). Cette dernière comporte une hélice souple (20) et un carter (40) pourvu d'un couvercle d'extrémité de pompe (50). Ce couvercle (50) est équipé d'un couvercle de sécurité transparent (52) pouvant être fixé au carter (50), d'un insert transparent thermorésistant (51) pouvant entrer en contact avec l'hélice (20) et d'un moyen d'espacement pour espacer l'insert (51) du couvercle de sécurité (52) et former une chambre (54).
PCT/AU1998/000264 1997-04-18 1998-04-16 Ameliorations de pompes a helices WO1998048172A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AU69112/98A AU722618B2 (en) 1997-04-18 1998-04-16 Improvements to impeller pumps
US09/403,246 US6213740B1 (en) 1997-04-18 1998-04-16 Flexible impeller pump having a transparent safety cover
EP98914704A EP0993554A4 (fr) 1997-04-18 1998-04-16 Ameliorations de pompes a helices

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AUPO6297A AUPO629797A0 (en) 1997-04-18 1997-04-18 Pump end cover
AUPO6297 1997-04-18

Publications (1)

Publication Number Publication Date
WO1998048172A1 true WO1998048172A1 (fr) 1998-10-29

Family

ID=3800592

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AU1998/000264 WO1998048172A1 (fr) 1997-04-18 1998-04-16 Ameliorations de pompes a helices

Country Status (3)

Country Link
EP (1) EP0993554A4 (fr)
AU (1) AUPO629797A0 (fr)
WO (1) WO1998048172A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6388417B1 (en) 1999-12-06 2002-05-14 Macrosonix Corporation High stability dynamic force motor
ITGE20110145A1 (it) * 2011-12-20 2013-06-21 Gianluigi Costa Girante per pompe e pompa comprendente detta girante
WO2014119932A1 (fr) * 2013-01-31 2014-08-07 한라비스테온공조 주식회사 Compresseur rotatif à palettes
WO2014123325A1 (fr) * 2013-02-05 2014-08-14 한라비스테온공조 주식회사 Compresseur rotatif à palette
RU174866U1 (ru) * 2017-01-20 2017-11-08 Сергей Андреевич Горбунов Роторопоршневая машина

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2076068A (en) * 1980-05-16 1981-11-25 Smith & Nephew Ass Peristaltic fluid-machines
DE4410800A1 (de) * 1994-03-29 1995-10-05 Mn Heizungsmontage Gmbh Drehanzeigeeinrichtung für Pumpen
US5563585A (en) * 1994-06-15 1996-10-08 See Water Inc. Water pump monitor
GB2307723A (en) * 1995-11-29 1997-06-04 Lee Deller Clearing air-locks, particularly in plumbing
WO1997043549A1 (fr) * 1996-05-17 1997-11-20 Tuthill Corporation Pompe volumetrique a main

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB365368A (en) * 1931-02-16 1932-01-21 August Frisch Apparatus for making visible the supply of liquid lubricants under pressure through pipes
US4573887A (en) * 1983-09-16 1986-03-04 S. E. Rykoff & Co. Corrosion-resistant roller-type pump
US5309716A (en) * 1991-01-02 1994-05-10 Kolbinger Herman J Rotary pump or engine with spherical body

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2076068A (en) * 1980-05-16 1981-11-25 Smith & Nephew Ass Peristaltic fluid-machines
DE4410800A1 (de) * 1994-03-29 1995-10-05 Mn Heizungsmontage Gmbh Drehanzeigeeinrichtung für Pumpen
US5563585A (en) * 1994-06-15 1996-10-08 See Water Inc. Water pump monitor
GB2307723A (en) * 1995-11-29 1997-06-04 Lee Deller Clearing air-locks, particularly in plumbing
WO1997043549A1 (fr) * 1996-05-17 1997-11-20 Tuthill Corporation Pompe volumetrique a main

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0993554A4 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6388417B1 (en) 1999-12-06 2002-05-14 Macrosonix Corporation High stability dynamic force motor
ITGE20110145A1 (it) * 2011-12-20 2013-06-21 Gianluigi Costa Girante per pompe e pompa comprendente detta girante
WO2014119932A1 (fr) * 2013-01-31 2014-08-07 한라비스테온공조 주식회사 Compresseur rotatif à palettes
WO2014123325A1 (fr) * 2013-02-05 2014-08-14 한라비스테온공조 주식회사 Compresseur rotatif à palette
US9822779B2 (en) 2013-02-05 2017-11-21 Hanon Systems Vane rotary compressor
RU174866U1 (ru) * 2017-01-20 2017-11-08 Сергей Андреевич Горбунов Роторопоршневая машина

Also Published As

Publication number Publication date
AUPO629797A0 (en) 1997-05-15
EP0993554A1 (fr) 2000-04-19
EP0993554A4 (fr) 2000-06-07

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