WO2019016520A1 - Pompe volumétrique rotative à membrane - Google Patents

Pompe volumétrique rotative à membrane Download PDF

Info

Publication number
WO2019016520A1
WO2019016520A1 PCT/GB2018/051969 GB2018051969W WO2019016520A1 WO 2019016520 A1 WO2019016520 A1 WO 2019016520A1 GB 2018051969 W GB2018051969 W GB 2018051969W WO 2019016520 A1 WO2019016520 A1 WO 2019016520A1
Authority
WO
WIPO (PCT)
Prior art keywords
diaphragm
housing
chamber
bearing
annular
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.)
Ceased
Application number
PCT/GB2018/051969
Other languages
English (en)
Inventor
William Eric SHEPHERD
Robert David FULLER
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.)
Charles Austen Pumps Ltd
Original Assignee
Charles Austen Pumps Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Charles Austen Pumps Ltd filed Critical Charles Austen Pumps Ltd
Priority to DK18745673.6T priority Critical patent/DK3655656T3/da
Priority to EP18745673.6A priority patent/EP3655656B1/fr
Priority to ES18745673T priority patent/ES2941464T3/es
Publication of WO2019016520A1 publication Critical patent/WO2019016520A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members
    • F04B43/0072—Special features particularities of the flexible members of tubular flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/12—Machines, pumps, or pumping installations having flexible working members having peristaltic action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/12—Machines, pumps, or pumping installations having flexible working members having peristaltic action
    • F04B43/14—Machines, pumps, or pumping installations having flexible working members having peristaltic action having plate-like flexible members
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C2/04—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of internal axis type

Definitions

  • the present invention relates to a rotary diaphragm positive displacement pump.
  • Such a rotary pump comprises a housing defining an annular chamber with inlet and outlet ports spaced apart around the chamber, a flexible annular diaphragm forming one side of the chamber spaced opposite an annular wall of the housing, the diaphragm being sealed at its edge to the housing, a partition extending across the chamber from a location between the inlet and outlet ports to the diaphragm; wherein the diaphragm is configured to be pressed progressively against the opposite wall of the housing to force fluid drawn in at the inlet port on one side of the partition around the chamber and to expel it at the outlet port at the other side of the partition.
  • a reinforcement ring to the diaphragm in order to add rigidity to a central portion of the diaphragm so that it can cope with higher loads and to prolong the lifetime of the pump.
  • the pump has been commercially successful for application such as medical analysis and water dispensing. All of these applications are at a relatively low pressure (typically below 200kPa but more normally below 100kPa). However, at higher pressures, the current design of pump has a more limited life span.
  • the present invention is directed to modified version of the pump to allow it to operate more reliable at higher pressures over a longer period of time.
  • a rotary pump as defined in claim 1 .
  • the present invention provides an advantage that the annular caps cannot be inserted so far into housing that they overly compress the diaphragm material. Further, both of the end caps can only be inserted to a limited degree and both can be inserted to the same degree. This provides for a more reliable assembly process ensuring alignment between all of the components and reliably forming the seal between the diaphragm and the housing.
  • the axial spacing is preferably no more than 0.4 mm and more preferably no more than 0.25 mm.
  • the second end is preferably formed with a groove at the radially outermost portion into which an inner part of the reinforcement ring can move in use. This allows the pump to accommodate a larger reinforcement ring thereby improving the robustness of the pump and providing an enhanced contact between the bearing and reinforcement ring.
  • the bearing may be a plain bearing or bushing. Alternatively, it may be a rolling element bearing such as ball bearing.
  • the configuration of the rotary pump is preferably such that the diaphragm does not rotate relative to the housing.
  • Fig. 1 is a cross section of the pump in a plane perpendicular to the axis of rotation which passes through the inlet and outlet ports;
  • Fig. 2 is an enlarged portion of Fig.1 showing the region adjacent to the outlet port;
  • Fig. 3 is a cross section in an axial plane shown as III - III in Fig. 1 which includes the line contact between the diaphragm and housing;
  • Fig 4 shows a detail of the bottom left hand region of Fig 3;
  • Fig 5 is a side view of the diaphragm
  • Fig 6 is an exploded perspective view of the diaphragm.
  • a tubular part of a rigid housing 1 has an annular groove 2 running around the inner surface, which acts as the pump chamber.
  • a flexible diaphragm 3 lies inside the wall of the housing leaving the groove free to contain the pumped fluid.
  • a rigid reinforcing ring 4 is moulded into the diaphragm and this ring is at all times in intimate contact with an outer surface of a bearing 5 mounted via an eccentric coupling 6 to a shaft 7 which extends through and is mounted in the housing in bearings (not shown).
  • the shaft 7 is mounted concentrically with the annular groove but eccentrically with regard to the axis 8 of the housing 1 and is powered by a motor (not shown).
  • the diaphragm would stretch and the performance would be reduced in a similar way to that experienced with peristaltic pumps, when the tubing collapses under vacuum.
  • the bearing 5, reinforcing ring 4 and central portion of the diaphragm 3 all orbit together inside the housing.
  • the two ends of the diaphragm 3 are clamped to the housing 1 by end caps 9, providing an effective and static seal to atmosphere.
  • line contact 10 exists between the diaphragm and the groove providing an abutment which pushes the fluid along towards the outlet port 1 1 and simultaneously draws fluid in through the inlet port 12.
  • the pump thus provides pressure and suction cycles at the output and intake respectively which are symmetrical and which vary sinusoidally. Since the diaphragm does not rotate relative to the housing, there is minimal sliding action between them and therefore almost no wear.
  • the end caps 9 are best shown in Fig 4. These have a first end 20 at the outermost face of the end cap and a second end 21 at the opposite innermost face. At the first end 20 is a radially outwardly extending flange 22 which, clamps the diaphragm 3 to the housing 1 with the cooperation of an annular flange 23 in the housing 1 . The flange 22 is then fixed to the housing 1 to hold it in place.
  • the end cap 9 has a tapered outer face 24 tapering inwardly away from the first end 20. This outer face 24 supports the diaphragm 3 when the diaphragm is in its radially innermost position as shown on the right hand side of Fig 3.
  • annular projection 25 At the radially innermost portion of the second end 21 is an annular projection 25.
  • the presence of this projection 25 forms a recess 26 which provides a step reduction in the outer diameter of the end cap 9 in the region adjacent to the second end 21 .
  • the second end 21 is spaced from the bearing 5 by a very small amount creating a first axial gap 27, in this case less than 0.4 mm and preferably 0.25 mm.
  • a second axial gap 28 is present between the recess 26 and the reinforcing ring 4. Again, this is less than 0.4 mm and preferably 0.25 mm.
  • the end cap 9 is located by engagement with the flange 22 against the flexible diaphragm 3.
  • the flange 22 cannot over compress the diaphragm 3 otherwise the end cap 9 will abut against the reinforcing ring 4 and bearing 5. This ensures that the end cap 9 at either end of the assembly can be inserted consistently as both end caps will compress the diaphragm 3 to the same limited amount.
  • the small nature of the second gap 28 also ensures that there is only a very small region of the compressible diaphragm 3 which remains unsupported as the diaphragm 3 is pressed against the end cap 9 (as shown in the right hand side of Fig 3). In this position, the opposite outer face of the diaphragm is receiving the full pressure within the pump chamber and this would tend it extrude the diaphragm material in any unsupported region on the opposite side.
  • the very small nature of this gap 28 significantly limits the potential for extrusion of the diaphragm 3 even when the pressure in the pump chamber is increased.
  • the reinforcement ring 4 has a modified shape as best shown in Figs. 3 and 4.
  • This comprises an embedded portion 30 forming the radially outermost portion of ring 4 and a support portion 31 forming the radially innermost portion of the ring 4.
  • the embedded portion 30 has a crenulated configuration in this case consisting of four annular ridges which, in cross section, have a curved configuration which is devoid of sharp corners. This is to avoid any stress concentrations in the ring 4. These crenulations are designed to provide a large surface area within a relatively limited axial region.
  • the diaphragm 3 is formed as an over mould on the ring 4 and the presence of the crenulations maximises the surface area for bonding between the two.
  • the relatively large number of rings 32 combined with their generally curved cross sections effectively spreads the load transmission between the two components thereby avoiding delamination of the two components even under relatively high loads.
  • the support portion 31 of the ring 4 extends axially beyond the crenulations 32 forming diaphragm support portions 34. These have a radially outwardly facing surface 35 which directly faces an inner face of the diaphragm 3.
  • the diaphragm 3 is not bonded to the face 35. However, in the position in which the diaphragm 3 is furthest from the housing 1 , the diaphragm is supported in this region by the face 35.
  • This feature provides support for the diaphragm at a time when it is under a relatively high inward pressure from the pressure within the pump chamber. As with the gap 28 mentioned above, this support prevents extrusion of the diaphragm material in this stressed position.
  • the outer face of the diaphragm 3 is provided with a trough 40 extended axially across a substantial portion of the diaphragm in the vicinity of the outlet.
  • a similar trough 41 is provided at the inlet.
  • the trough 40 in each case has a first edge 42 adjacent to the partition 13 and a second edge 43 opposite to the first edge.
  • the troughs 40, 41 are aligned with a respective outlet duct 44 and inlet duct 45 which lead to the outlet port 1 1 and from the inlet port 12 respectively.
  • troughs 40, 41 In the absence of these troughs 40, 41 when the diaphragm 3 is in the uppermost position, it is possible that while under high pressure, the diaphragm material will extrude into the port to a limited extent thereby causing damage to the diaphragm over time.
  • the presence of the troughs 40, 41 reduces or eliminates this effect.
  • trough terminates at edge 43 which is adjacent to the edge of duct 44 so that the full thickness of the diaphragm is available immediately downstream of the edge 43. This means that the diaphragm is able to fully engage with the housing 1 as the diaphragm reaches the top of its travel thereby ensuring that the point contact 10 is maintained up until the outlet duct 44 in order to expel the liquid.
  • reinforcing members 50 are best shown in Figs. 2, 5 and 6. Although two such reinforcing members 50 are shown in Fig. 6, only one of these need be present in practice. This would depend upon the direction in which the partition 13 is loaded in use.
  • the reinforcing member 50 comprises a frame of material which is harder than the material of the partition and therefore more resistant to deflection under pressure. This is shaped to fit in a shallow recess 51 in the side of the partition. It is preferably a press fit but may be, more securely attached if the application requires it. As shown best in Figure 6, the geometry of the reinforcing member 50 is such that it may be considered as a reinforcing plate, whose thickness is much smaller than its length/width.
  • the partition 13 deflects to some extent in order to accommodate this orbital movement.
  • the pressure of the fluid in the inlet 12 or outlet 1 1 will also act to deflect the partition. Under higher pressure loads, this can cause the softer material of the diaphragm to contact the walls 14, 15 thereby wearing the diaphragm material, particularly at the bottom edge of the walls 14, 15 which can dig into the diaphragm 3 material.
  • the reinforcing member 50 is positioned in the vicinity of the bottom edge of the walls 14, 15 such that any contact will be between two harder surfaces thereby protecting the diaphragm material from wear.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe rotative comprenant un boîtier (1) définissant une chambre annulaire avec des orifices d'entrée et de sortie (12, 11) espacés autour de la chambre, une membrane (3) annulaire souple formant un côté de la chambre, ledit côté étant espacé à distance d'une paroi annulaire du boîtier (1) et ayant deux extrémités circulaires opposées, la membrane (3) étant rendue étanche au niveau de ses bords avec le boîtier (1), une cloison (13) s'étendant entre les orifices d'entrée et de sortie (12, 11) vers la membrane (3). La membrane (3) est conçue pour être pressée progressivement contre le boîtier (1), par un moyen de rotation, pour forcer le fluide autour de la chambre. Le moyen de rotation comprend un support (5). Un anneau de renfort (4) entoure le support (5) et est relié à une région centrale de la membrane (3) et à une paire d'embouts (9) annulaires, chaque embout se trouvant à chaque extrémité de la membrane (3). Chaque embout (9) est axialement espacé de moins de 0,5 mm du support (5) adjacent ou de l'anneau de renfort (4).
PCT/GB2018/051969 2017-07-19 2018-07-11 Pompe volumétrique rotative à membrane Ceased WO2019016520A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DK18745673.6T DK3655656T3 (da) 2017-07-19 2018-07-11 Positiv fortrængningspumpe med roterende membran
EP18745673.6A EP3655656B1 (fr) 2017-07-19 2018-07-11 Pompe à déplacement positif à diaphragme rotatif
ES18745673T ES2941464T3 (es) 2017-07-19 2018-07-11 Una bomba giratoria de desplazamiento positivo de diafragma

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB1711608.8 2017-07-19
GB1711608.8A GB2564680B (en) 2017-07-19 2017-07-19 A rotary diaphragm positive displacement pump

Publications (1)

Publication Number Publication Date
WO2019016520A1 true WO2019016520A1 (fr) 2019-01-24

Family

ID=59713462

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB2018/051969 Ceased WO2019016520A1 (fr) 2017-07-19 2018-07-11 Pompe volumétrique rotative à membrane

Country Status (5)

Country Link
EP (1) EP3655656B1 (fr)
DK (1) DK3655656T3 (fr)
ES (1) ES2941464T3 (fr)
GB (1) GB2564680B (fr)
WO (1) WO2019016520A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR860457A (fr) * 1939-06-26 1941-01-16 Pompe à membrane tubulaire
GB854610A (en) * 1959-04-13 1960-11-23 Adolf Roebig Rotary pump
GB1280185A (en) * 1968-08-09 1972-07-05 Siegfried Stauber Rotary positive displacement pump
US4332534A (en) * 1978-12-14 1982-06-01 Erich Becker Membrane pump with tiltable rolling piston pressing the membrane

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB785597A (en) * 1955-08-16 1957-10-30 Reginald Clarence Ford Improvements in rotary pumps
JPS56143385A (en) * 1980-04-09 1981-11-09 Kazuichi Ito Rotary pump
GB9614866D0 (en) * 1996-07-15 1996-09-04 Charles Austen Pumps Ltd Rotary pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR860457A (fr) * 1939-06-26 1941-01-16 Pompe à membrane tubulaire
GB854610A (en) * 1959-04-13 1960-11-23 Adolf Roebig Rotary pump
GB1280185A (en) * 1968-08-09 1972-07-05 Siegfried Stauber Rotary positive displacement pump
US4332534A (en) * 1978-12-14 1982-06-01 Erich Becker Membrane pump with tiltable rolling piston pressing the membrane

Also Published As

Publication number Publication date
GB201711608D0 (en) 2017-08-30
ES2941464T3 (es) 2023-05-23
GB2564680B (en) 2019-08-21
EP3655656A1 (fr) 2020-05-27
GB2564680A (en) 2019-01-23
DK3655656T3 (da) 2023-05-01
EP3655656B1 (fr) 2023-03-22

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