US20050053476A1 - Diaphragm pump system - Google Patents

Diaphragm pump system Download PDF

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Publication number
US20050053476A1
US20050053476A1 US10/842,626 US84262604A US2005053476A1 US 20050053476 A1 US20050053476 A1 US 20050053476A1 US 84262604 A US84262604 A US 84262604A US 2005053476 A1 US2005053476 A1 US 2005053476A1
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US
United States
Prior art keywords
pressure
pump
intensifier
supply
diaphragm pump
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.)
Abandoned
Application number
US10/842,626
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English (en)
Inventor
Nigel Wood
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.)
ITW Ltd
Original Assignee
ITW 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 ITW Ltd filed Critical ITW Ltd
Assigned to ITW LIMITED reassignment ITW LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WOOD, NIGEL CHARLES
Publication of US20050053476A1 publication Critical patent/US20050053476A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • F04B43/0736—Pumps having fluid drive the actuating fluid being controlled by at least one valve with two or more pumping chambers in parallel
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
    • F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
    • F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
    • F04B9/133—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting elastic-fluid motor

Definitions

  • This invention relates to a pumping system incorporating a diaphragm pump, particularly but not exclusively for supplying liquid paint to a paint spraying system.
  • Diaphragm pumps are well known and generally comprise a pumping chamber bounded in part by a moveable diaphragm, the diaphragm being moveable by the application of fluid under pressure to reduce the volume of the pumping chamber and so expel fluid, usually liquid, from the pumping chamber.
  • diaphragm pumps are constructed as double-acting pumps in that there are two pumping chambers each having an associated diaphragm, the two diaphragms being physically interconnected so that when one is moving to reduce the size of its pumping chamber to expel fluid from the pumping chamber the opposite diaphragm is moving in a direction to increase the volume of the pumping chamber and so draw fluid from a fluid supply into the pumping chamber.
  • the fluid being pumped by a diaphragm pump is a liquid, and also, conventionally, the pressurised fluid applied to the diaphragms to cause them to perform their pumping strokes is compressed air.
  • diaphragm pumps exhibit a 1:1 pressure ratio in that air at 1 bar pressure is applied to the pump to drive the pump, producing a liquid pressure in the output line of the pump which is also 1 bar. It is known to provide diaphragm pumps with an increased pressure ratio in that, for example, a 1 bar air pressure driving the pump produces a 3 bar output pressure in the liquid output line of the pump.
  • diaphragm pumps are significantly larger and more expensive to produce than are pumps which have a 1:1 ratio, their use in systems in accordance with the present invention is not excluded. For convenience hereinafter in this specification it is assumed that the pump has a 1:1 ratio.
  • a pumping system incorporating a diaphragm pump and in association therewith a pressure intensifier receiving pressurised driving fluid from a supply, the intensifier boosting the pressure of the drive fluid beyond its supply pressure and supplying the drive fluid, at said increased pressure, to said diaphragm pump, to generate pumping strokes of the pump producing a pump output pressure in excess of the drive fluid supply pressure.
  • said pressure intensifier is at least a two times intensifier (preferably a 2.5 times intensifier) and conveniently the pump has a 1:1 input to output pressure ratio whereby the pressure in the output line of the pump is two times (preferably 2.5 times) the supply pressure of the drive fluid to the pressure intensifier.
  • the pressure intensifier is incorporated into the diaphragm pump.
  • the diaphragm pump is a double-acting diaphragm pump and the pressure intensifier is incorporated in a spool valve controlling the supply of drive fluid to the diaphragms of the double-acting diaphragm pump.
  • the diaphragm pump has a 1:1 input to output pressure ratio.
  • FIG. 1 is a diagrammatic cross-sectional view of a double-acting diaphragm pump
  • FIGS. 2 and 3 are diagrammatic representations of part of the pump of FIG. 1 showing how the pump operates;
  • FIGS. 4 and 5 are diagrammatic cross-sectional views of alternative constructions of pressure intensifier for use in combination with the diaphragm pump of FIGS. 1, 2 and 3 .
  • FIGS. 1, 2 and 3 illustrate a known form of diaphragm pump in which a generally cylindrical central metal body 11 has an axial through bore 12 and is fitted, at its opposite ends respectively, with first and second end plates 13 , 14 .
  • the face of the body 11 presented to the end plate 13 is concave, and the face of the end plate 13 presented towards the body 11 is also concave.
  • the concavities of the end plate 13 and body 11 define an internal chamber which is divided into a drive chamber 15 and a pumping chamber 16 by a flexible metal diaphragm 17 having its periphery trapped between peripheral regions of the end plate 13 and the body 11 .
  • the arrangement at the opposite axial end of the body 11 is similar in that an internal chamber is divided into a drive chamber 15 a and a pumping chamber 16 a by means of a diaphragm 17 a .
  • a link rod 18 is slidably received in the bore 12 of the body and is connected at its opposite axial ends respectively to the diaphragms 17 , 17 a .
  • the rod 18 passes through the respective diaphragm and diaphragm control washers 19 , 21 of different diameter are clamped against opposite faces of the diaphragm by a nut 22 engaged on a screw threaded end region of the rod 18 .
  • the diaphragm pump illustrated in FIG. 1 is designed to be driven by compressed air, and to pump a liquid paint. The references to drive air, and pumped liquid will be retained throughout the remainder of this application, but it is to be understood that there may be applications in which fluids other than liquid paint are pumped, and fluids other than compressed air are used to power the pump.
  • Each end plate 13 , 14 includes a liquid inlet passage 23 which communicates with its respective pumping chamber 16 , 16 a through a non-return valve 24 conveniently in the form of a ball check valve.
  • each end plate 13 , 14 includes a liquid outlet passage 25 communicating with the respective chamber 16 , 16 a through a non-return valve 26 also conveniently in the form of a ball check valve.
  • the liquid inlet passage of the end plate 14 has an open union 27 whereby the inlet passage can be connected to a supply of liquid to be pumped in use.
  • the inlet passage of the end plate 14 upstream of the respective non-return valve, is coupled to the inlet passage 23 of the end plate 13 upstream of the non-return valve 24 by a transverse passage 28 extending axially within the body 11 .
  • the liquid outlet passage 25 of the end plate 23 has an open union 29 for connection to the arrangement to be supplied with pumped liquid, for example a paint spraying system.
  • the union 29 is downstream of the non-return valve 26 of the end plate 13 and a transverse passage 31 parallel to the passage 28 , extends within the body 11 axially to interconnect the liquid outlet passage of the end plate 14 , downstream of its non-return valve, with the passage 25 of the end plate 13 downstream of the non-return valve 26 .
  • liquid enters the double-acting diaphragm pump through the union 27 to be pumped either from the chamber 16 , or the chamber 16 a , and irrespective of which chamber is performing a pumping stroke, the pumped liquid issues from the pump by way of the union 29 .
  • the rod 18 forms part of a spool valve 32 controlling the admission of compressed air to the drive chambers 15 , 15 a of the pump.
  • the spool valve 32 forms part of a change-over valve arrangement of the pump and operates in combination with a change-over valve 33 the housing of which forms part of, or is secured to, the body 11 .
  • the change-over valve 33 has a first operative position (as shown in FIG. 2 ) to which it is urged by the application of compressed air to one end of the valve, and a second operative position (as shown in FIG. 3 ) to which it is urged by a return spring 34 of the valve.
  • a compressed air inlet port 35 of the spool valve 32 is supplied with compressed air from a standardised mains supply (indicated at “B” in FIGS. 2 and 3 ) associated with the liquid pumping system.
  • the pressure at the standardised supply line B is 5 bar.
  • An air pressure inlet port 36 of the valve 33 is supplied with compressed air from the standard mains supply through the intermediary of a pressure intensifier 37 ( FIG. 4 ).
  • the pressure intensifier 37 is a 2.5 times intensifier, and so the pressure in a supply line “A” from the intensifier 37 to the inlet port 36 is 12.5 bar.
  • FIG. 2 illustrates the double-acting diaphragm pump at the right-hand end of its travel, in which the diaphragm 17 a has moved towards the end plate 14 so that the chamber 16 a has undergone a pumping stroke.
  • the spool valve 32 places the port 35 in communication with an outlet port 38 coupled to the pressure sensing port of the valve 33 .
  • Mains supply air pressure applied to the valve 33 from the port 38 of the body 11 drives the valve 33 against the spring 34 to a position in which the intensified supply “A” is connected through a line 39 to the chamber 15 of the pump and at the same time the chamber 15 a is connected through a line 41 and the valve 33 to atmosphere so that pressure in the chamber 15 a can be exhausted.
  • compressed air at 12.5 bar is supplied through the valve 33 to the chamber 15 driving the piston 17 to the left carrying with it the rod 18 and the piston 17 a .
  • Liquid within the chamber 16 is expelled by this movement of the diaphragm 17 and flows from the chamber 16 through the non-return valve 26 and the pressure supply port 29 of the pump.
  • the non-return valve 24 on the inlet side of the chamber 16 remains firmly closed and thus the left-hand end of the pump (as drawn in FIG. 1 ) performs a pumping stroke. Simultaneously the chamber 16 a at the right hand end of the pump is undergoing reduced pressure as the volume of the chamber 16 a is increased and so the non-return valve at the outlet side of the chamber 16 a remains firmly closed, but the non-return valve at the inlet side of the chamber 16 a opens to permit fresh liquid to be drawn into the chamber 16 a from the liquid supply port 27 .
  • the spool valve 32 moving with the rod 18 , achieves a position in which the pressure sensing port of the valve 33 is connected to an exhaust port 44 of the body 11 and the position of the change-over valve 33 switches, under the influence of the spring 34 , to place the line 39 in communication with atmosphere through the valve 33 and to place the line 41 in communication with the intensified air pressure at “A”.
  • the chamber 15 a is now supplied with pressure and so the diaphragm 17 a performs a pumping stroke while the diaphragm 17 is retracted, increasing the volume of the chamber 16 , and allowing liquid to be drawn from the inlet union 27 through the passage 28 and the valve 24 into the chamber 16 .
  • the liquid pumped from the chamber 16 a by movement of the diaphragm 17 a flows through the non-return valve at the outlet of the chamber 16 a and through the passage 31 to the outlet union 29 of the pump.
  • the pump continues to reciprocate in the above manner under the control of the spool valve 32 and change-over valve 33 as long as there is compressed air at “A” and “B”.
  • the pump is a 1:1 pump and the air pressure applied to the diaphragms 17 , 17 a is 12.5 bar, then liquid is pumped from the union 29 nominally (ignoring usual operating losses) at 12.5 bar.
  • the 2.5 times pressure intensifier 37 illustrated in FIG. 4 is of known, commercially available form, and will be connected between the standard mains air pressure supply of the system and the port 36 of the change-over valve 33 . It is anticipated however that a pressure intensifier fulfilling the same function as the intensifier 37 can be mechanically incorporated into the change-over system consisting of the spool valve 32 and the change-over valve 33 thereby minimising the component count of the system, and ensuring that the pump incorporates the pressure intensifier, and so can simply be coupled to an existing compressed air and liquid supply arrangement.
  • the intensifier shown in FIG. 4 utilizes pistons of different diameter appropriately dimensioned to effect pressure intensification at 2.5:1. It is to be understood that while pressure intensification of about 2:1 is desired for the above described paint spraying system, other applications may require other pressure intensification ratios. The skilled man will recognise that other ratios can be achieved using intensifiers based upon the FIG. 4 design with their relative dimensions adjusted according to the required ratio.
  • FIG. 5 shows an alternative intensifier design arranged using pistons of equal diameter to achieve a 2:1 pressure intensification ratio, which could be substituted for the FIG. 4 design in an appropriate application.
  • the construction and operation-of the intensifiers of FIGS. 4 and 5 will be well understood by the skilled man.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US10/842,626 2003-05-13 2004-05-11 Diaphragm pump system Abandoned US20050053476A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0310942.8A GB0310942D0 (en) 2003-05-13 2003-05-13 Diaphragm pump system
GB0310942.8 2003-05-13

Publications (1)

Publication Number Publication Date
US20050053476A1 true US20050053476A1 (en) 2005-03-10

Family

ID=9957952

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/842,626 Abandoned US20050053476A1 (en) 2003-05-13 2004-05-11 Diaphragm pump system

Country Status (14)

Country Link
US (1) US20050053476A1 (zh)
EP (1) EP1477674B1 (zh)
JP (1) JP2004340149A (zh)
KR (1) KR20040097936A (zh)
CN (1) CN1621686A (zh)
AT (1) ATE345443T1 (zh)
AU (1) AU2004202021B2 (zh)
BR (1) BRPI0402047A (zh)
CA (1) CA2466844C (zh)
DE (1) DE602004003167T2 (zh)
ES (1) ES2277206T3 (zh)
GB (1) GB0310942D0 (zh)
MX (1) MXPA04004509A (zh)
TW (1) TWI259238B (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070193797A1 (en) * 2006-02-22 2007-08-23 Shamis Dmitry A Pressure booster system

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007262911A (ja) * 2006-03-27 2007-10-11 Asahi Sunac Corp 塗料圧送システム及び塗料圧送方法
JP5052995B2 (ja) 2007-08-21 2012-10-17 アルバック機工株式会社 ダイアフラムポンプ
JP5139405B2 (ja) 2009-12-03 2013-02-06 株式会社ヤマダコーポレーション ポンプ用バルブ本体
KR101138133B1 (ko) * 2010-05-19 2012-04-23 배방희 다이아프램 펌프구동유닛 및 이를 이용한 다이아프램 펌프
JP6231844B2 (ja) * 2013-10-11 2017-11-15 日東精工株式会社 吸引ポンプ
CN104912780A (zh) * 2015-05-27 2015-09-16 张伟伟 气动隔膜泵抽取液体的方法
WO2019106674A1 (en) * 2017-11-29 2019-06-06 Serenno Medical A dual active valve fluid pressure operated positive displacement pump

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3583832A (en) * 1969-05-13 1971-06-08 Lee Co Booster
US4548551A (en) * 1983-05-10 1985-10-22 T.M.B. Fertilizer Pumps Ltd. Fluid driven reciprocating pump capable of either single-action or double-action operation
US4728267A (en) * 1986-02-19 1988-03-01 T.M.B. Fertilizer Pumps Ltd. Fluid driven reciprocating pump
US5277555A (en) * 1992-12-31 1994-01-11 Ronald L. Robinson Fluid activated double diaphragm pump
US5332372A (en) * 1992-04-20 1994-07-26 Warren Rupp, Inc. Modular double-diaphragm pump
US5368452A (en) * 1993-07-20 1994-11-29 Graco Inc. Double diaphragm pump having two-stage air valve actuator
US5927954A (en) * 1996-05-17 1999-07-27 Wilden Pump & Engineering Co. Amplified pressure air driven diaphragm pump and pressure relief value therefor
US6004105A (en) * 1998-02-23 1999-12-21 Warren Rupp, Inc. Diaphragm pump with adjustable stroke length
US6036445A (en) * 1998-02-27 2000-03-14 Warren Rupp, Inc. Electric shifting mechanism/interface for fluid power diaphragm pumps

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5325903A (en) * 1976-08-23 1978-03-10 Tokyo Ai Ii Shii Kk Hydraulicallyyopetated diaphragm pumps
JPS59144203U (ja) * 1983-03-17 1984-09-27 エスエムシ−株式会社 増圧空気供給装置
JPH0519591Y2 (zh) * 1987-05-21 1993-05-24
JPH0244066Y2 (zh) * 1987-05-25 1990-11-22
JPH0660782U (ja) * 1993-01-28 1994-08-23 岩田塗装機工業株式会社 ２段ダイアフラムポンプ
AU714861B2 (en) * 1995-09-18 2000-01-13 World Wide Systems (NZ) Limited A fluid pressure driven pumping system

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3583832A (en) * 1969-05-13 1971-06-08 Lee Co Booster
US4548551A (en) * 1983-05-10 1985-10-22 T.M.B. Fertilizer Pumps Ltd. Fluid driven reciprocating pump capable of either single-action or double-action operation
US4728267A (en) * 1986-02-19 1988-03-01 T.M.B. Fertilizer Pumps Ltd. Fluid driven reciprocating pump
US5332372A (en) * 1992-04-20 1994-07-26 Warren Rupp, Inc. Modular double-diaphragm pump
US5277555A (en) * 1992-12-31 1994-01-11 Ronald L. Robinson Fluid activated double diaphragm pump
US5368452A (en) * 1993-07-20 1994-11-29 Graco Inc. Double diaphragm pump having two-stage air valve actuator
US5927954A (en) * 1996-05-17 1999-07-27 Wilden Pump & Engineering Co. Amplified pressure air driven diaphragm pump and pressure relief value therefor
US6004105A (en) * 1998-02-23 1999-12-21 Warren Rupp, Inc. Diaphragm pump with adjustable stroke length
US6036445A (en) * 1998-02-27 2000-03-14 Warren Rupp, Inc. Electric shifting mechanism/interface for fluid power diaphragm pumps

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20070193797A1 (en) * 2006-02-22 2007-08-23 Shamis Dmitry A Pressure booster system

Also Published As

Publication number Publication date
GB0310942D0 (en) 2003-06-18
CN1621686A (zh) 2005-06-01
ES2277206T3 (es) 2007-07-01
AU2004202021B2 (en) 2006-10-05
JP2004340149A (ja) 2004-12-02
TWI259238B (en) 2006-08-01
DE602004003167D1 (de) 2006-12-28
AU2004202021A1 (en) 2004-12-02
KR20040097936A (ko) 2004-11-18
EP1477674A1 (en) 2004-11-17
BRPI0402047A (pt) 2005-02-22
DE602004003167T2 (de) 2007-09-06
MXPA04004509A (es) 2005-06-08
EP1477674B1 (en) 2006-11-15
CA2466844A1 (en) 2004-11-13
ATE345443T1 (de) 2006-12-15
CA2466844C (en) 2008-12-23

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Date Code Title Description
AS Assignment

Owner name: ITW LIMITED, UNITED KINGDOM

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WOOD, NIGEL CHARLES;REEL/FRAME:015389/0832

Effective date: 20040507

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION