EP0147889A1 - Pompe à diaphragmes actionnée par l'air et soupape pour cette pompe - Google Patents

Pompe à diaphragmes actionnée par l'air et soupape pour cette pompe Download PDF

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Publication number
EP0147889A1
EP0147889A1 EP84201842A EP84201842A EP0147889A1 EP 0147889 A1 EP0147889 A1 EP 0147889A1 EP 84201842 A EP84201842 A EP 84201842A EP 84201842 A EP84201842 A EP 84201842A EP 0147889 A1 EP0147889 A1 EP 0147889A1
Authority
EP
European Patent Office
Prior art keywords
bore
diaphragm pump
valve member
characterizedin
valve
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.)
Withdrawn
Application number
EP84201842A
Other languages
German (de)
English (en)
Inventor
Joseph Candido Casilli
Lawrence Joseph Gibson
William De Witt Hessler
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.)
TDK Micronas GmbH
ITT Inc
Original Assignee
Deutsche ITT Industries GmbH
ITT Industries Inc
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
Priority claimed from US06/564,947 external-priority patent/US4555222A/en
Priority claimed from US06/564,944 external-priority patent/US4494574A/en
Application filed by Deutsche ITT Industries GmbH, ITT Industries Inc filed Critical Deutsche ITT Industries GmbH
Publication of EP0147889A1 publication Critical patent/EP0147889A1/fr
Withdrawn legal-status Critical Current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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L23/00—Valves controlled by impact by piston, e.g. in free-piston machines

Definitions

  • the present invention relates to pumps in general and, more particularly, to air-operated diaphragm pumps and to valve arrangements therefor.
  • pumps there are already known various constructions of pumps, among them such which are particularly suited for pumping liquids with high viscosity, such as paint or the like.
  • Some of the known pumps are constructed as diaphragm pumps in which compressed air or similar gaseous medium is being used for achieving the pumping action.
  • a movable wall including a flexible diaphragm extends across the internal space of the pump casing to sealingly subdivide such interior into a pumping chamber for the liquid to be pumped and an actuating chamber into which the pressurized gaseous medium is admitted to exert its pressure on the movable wall and from which it is discharged, thus to achieve the pumping action.
  • Such diaphragm pumps are often used in tandem, that is, two of such pumps are being used at the same time, these pumps having their movable walls connected for movement in unison so that, while one of the diaphragm pumps has the pressurized gaseous fluid admitted into its actuating chamber and thus pumps the liquid, the contents of the actuating chamber of the other pump is discharged as the movable wall moves in unisbn with the first-mentioned pump movable wall and, hence, additional liquid is being drawn into the pumping chamber of the latter pump.
  • the pressurized gaseous medium contains any contaminants,-such as particles of dust or the like, such contaminants will be captured by the lubricant and thus perform an abrading function in the valve arrangement, which will result in excessive wear of the various components of the latter.
  • Still another object of the present invention is so to construct the pumping arrangement of the type here under consideration that the timing of the distribution of the gaseous medium is controlled in dependency on the extent of movement of the movable walls of the tandem diaphragm pumps.
  • a concomitant object of the present invention is so to design the valve arrangement as to be simple in construction, inexpensive to manufacture, easy to use, and reliable in operation nevertheless.
  • one feature of the present invention resides in a pumping arrangement of the above type, with two diaphragm pumps arranged and operating in tandem, wherein two limiting valve assemblies are accommodated in respective bores of the housing of the control valve arrangement and have stem portions that extend into the respective actuating chambers and into the paths of movement of the respective movable walls.
  • These control valve assemblies control the admission of pressurized gaseous medium to, and its discharge from, the spaces adjacent to the axial ends of a distributing valve which controls the admission and discharge of pressurized gaseous medium to and from the actuating chambers.
  • the limiting valve assembly In one end position of the limiting valve assembly, into which it is urged by a spring, the limiting valve assembly connects the respective space with the discharge conduit and thus with the ambient atmosphere. In the other end position, the limiting valve assembly connects the space with the supply of the pressurized gaseous medium.
  • the distributing valve body which is configurated as a spool, is thus shifted between its terminal positions to alternatingly admit the pressurized medium into and discharge the same from the actuating chambers.
  • the housing of the control arrangement is made of aluminum, and the surface bouncing the bore receiving the spool has a hard anodized coating thereon. At least that portion of spool which comes in contact with the hard anodized coating is-made of a self-lubricating material.
  • the spool carries, in respective grooves thereof, respective separating rings which are also made of a material that is self-lubricating.
  • the pump 1 includes, as its main components, a support or frame 2, two pumping arrangements 3 and 4, and an actuating and control arrangement 5 interposed between the two pumping arrangements 3 and 4 and controlling the operation thereof in a manner which will be discussed in greater detail later.
  • the support or frame 2 is hollow to bound a plurality of passages cr compartments yet to be described.
  • the frame 2 is provided with a suction or inlet port 6 for the fluid to be pumped, while a discharge or outlet port 7 for the fluid being pumped is arranged at the upper portion of the frame 2.
  • the inlet port 6 communicates with two inlet passages 8 and 9, and the outlet port 7 communicates with two outlet passages 10 and 11.
  • the inlet passages 8 and 9 open into respective inlet valve compartments 12 and 13 that -accommodate respective inlet valve balls 14 and 15 and communicate, via respective apertures 16 and 17, with respective pumping chambers 18 and 19.
  • annular sealing elements 20 and 21 of elastic material are stationarily arranged at the lower portions of the respective compartments 12 and 13 to serve as valve seats for the respective valve balls 14 and 15.
  • the pumping chambers 18 and 19 respectively communicate, at their upper ends, with outlet valve compartments 22 and 23 which, in turn, communicate with the respective outlet passages 10 and 11 via apertures 24 and 25.
  • the outlet valve compartments 22 and 23 accommodate respective outlet valve balls 26 and 27 as well as, at their lower parts, respective annular sealing elements 28 and 29 constituting valve seats for the respective outlet valve balls 26 and 27.
  • the frame 2 is shown to be constituted by separate lateral parts 31 and 32, and upper and lower transverse parts 33 and 34 which extend between and interconnect the lateral parts 31 and 32.
  • the parts 31 to 34 are connected to one another by respective annular clamping elements 35, 36, 37 and 38 which are of well known construction that needs no elaboration here.
  • the annular sealing elements 20, 21, 28 and 29 are arranged at the parting planes between the various parts 31 to 34 of the frame 2 so that, besides acting as the valve seats for the respective valve balls 14, 15, 26 and 27, they also seal tne interfaces between the parts 31 to 34 of the frame 2, by being confined and hence held in position between the parts 31 to 34 by the action of the respective clamping elements 35 to 38.
  • the lateral portions 31 and 32 of the frame 2 have respective extensions or flanges 39 and 40.
  • the pumping arrangements 3 and 4 include casings or shells 41 and 42 which are secured, in a conventional manner which is not specifically shown in the drawing, such as by screws or similar connectors, to the control arrangement 5, and which are respectively connected, by means of annular clamping elements 43 and 44, to the flanges 39 and 40 of the lateral portions 31 and 32 of the frame 2.
  • the shells 41 and 42 define with the associated lateral portions 31 and 32 respective internal spaces. Each of these internal spaces is subdivided by a respective movable wall 45 and 46 into the aforementioned pumping chamber 31 or 32, and an actuating chamber 47 or 48.
  • the respective movable wall 45 or 46 includes a respective flexible diaphragm 49 or 50 which is sealingly clamped at its outer periphery between the . flange 39 or 40 and the shell 41 or 42 by the action of the respective clamping element 43 or 44.
  • each of the diaphragms 49 or 50 is sealingly secured to a common shaft 51 that passes through the interior of the control arrangement 5 and interconnects the two movable walls 45 and 46 for movement in unison.
  • To mount the respective diaphragms 49 and 50 on the common shaft 51 there are provided two mounting plates 52 and 53, or 54 and 55, on the common shaft 51, which confine the central region of the respective diaphragm 49 or 50 between themselves.
  • the mounting plates 52 and 53, or 54 and 55 are mounted on the common shaft 51 by being confined between a respective shoulder 56 or 58, and a threaded fastener 57 or 59, such as a nut.
  • the mounting plates 52 and 53, or 54 and 55 clamp the central region of the respective diaphragm 49 or 50 between themselves to mount the diaphragms 49 and 50 to the common shaft 51.
  • control arrangement 5 controls the admission of an actuating medium, especially a gaseous medium such as compressed air, into the actuating compartments or chambers 47 and 48, and the discharge of such an actuating medium from the actuating chambers 47 and 48.
  • an actuating medium especially a gaseous medium such as compressed air
  • the movable walls 45 and 46 are approaching the end of their rightward stroke. This is achieved by admitting the pressurized actuating medium into the actuating chamber 48 of the pumping arrangement 4, while simultaneously allowing the contents of the actuating chamber 47 of the pumping arrangement 3 to escape from the actuating chamber 47 at a rather low superatmospheric pressure. Because of the pressure exerted by the pressurized actuating medium on the movable wall 46, and the relatively low resistance offered by the pressure of the medium contained in the actuating chamber 47 on the movable wall 45, the shaft 51 and the movable walls 45 and 46 mounted thereon are caused to move in the rightward direction.
  • control arrangement 5 controls the flow of the actuating medium in and out of the actuating chambers 47 and 48.
  • a first and a second version of the construction of the control arrangement 5 will now be particularly described in connection respectively with Figs. 2 and 4 of the drawing, and their operation will then be described particularly in connection respectively with Figs. 3 and 5 of the drawing.
  • These versions are similar to one another in many respects so that the same reference numerals will be used to identify corresponding parts. Both versions will be jointly discussed below and only the differences between them will be particularly pointed out.
  • Fig. 2 and 4 are respective exploded views of the first and second versions of the control arrangement 5 showing the various components constituting the same.
  • One of the main components of the control arrangement 5 is a housing 60 through which the common shaft 51 passes, as shown, substantially centrally, being supported in a self lubricated sliding hearing or bearings 30.
  • the housing 60 has three bores 61, 62 and 63 which are indicated to extend substantially parallel at the axis of the common shaft 51, and at a radial spacing therefrom.
  • the bore 62 could extend transversely of the housing 60 if so desired, for instance, in order to reduce the overall dimensions and the weight of the housing 60.
  • the bore 62 serves for receiving a distributing valve body 64 which is constructed as a spool valve.
  • the distributing valve body 64 is provided with two distributing channels 65 and 66 separated from one another by a separating collar 67 and delimited at their other axial ends by respective delimiting collars 68 and 69.
  • the distributing valve body 64 further includes, at its respective axial ends, terminal collars 70 and 71 which bound respective grooves 72 and 73 between themselves and the respective delimiting collars 68 and 69 .
  • Resilient expansion rings 74 and 75 are received in the respective grooves 72 and 73 in the assembled condition of the valve body 64, these expansion rings 74 and 75 being surrounded by respective split separating rings 76 and 77 which are also received in the respective grooves 72 and 73 at least when the distributing valve body 64 is accommodated in the bore 62.
  • the bores 61 and 63 accommodate respective switching or limiting valve assemblies 78 and 79 which are structually identical so that the various components thereof will be identified by the same reference numerals in the following description and the drawing.
  • the respective switching valve assembly 78 or 79 includes, as one of its main components, a switching valve member 80 which includes a guiding portion 81 and a stem portion 82 at one end of the guiding portion 81.
  • the guiding portion 81- is shown to be hexagonal in cross-section. The reason for this cross-sectional configuration will be given later.
  • the stem portion 82 of the first version is -provided with a groove 83 that serves to partially accommodate an abutment washer 84.
  • abutment washer 84 there are arranged, around part of the stem portion 82 which extends between the groove 83 and the guiding portion 81, in succession, a spring washer 85, a separating washer 86, a sealing ring 87, and an additional sealing ring 88.
  • a spring washer 85 there are arranged, around part of the stem portion 82 which extends between the groove 83 and the guiding portion 81, in succession, a spring washer 85, a separating washer 86, a sealing ring 87, and an additional sealing ring 88.
  • the sealing ring 88 is provided being arranged around the stem portion 82 upon assembly.
  • a helical compression spring 89 is accommodated in the respective bore 61 or 63 at the opposite axial end of the guiding portion 81 from the stem portion 82.
  • Figs. 2 and 4 also indicates that an annular element 90 is arranged at one axial end of the bore 63.
  • another such annular element 90 is arranged in the bore 61, but at the opposite axial end thereof.
  • the housing 60 has an internally threaded discharge bore 91, and that a discharge nipple or connector 92 having an externally threaded end portion is threaded into the bore 91 in its assembled condition.
  • the housing 60 also has a feeding nipple or connector similar to the discharge nipple or connector 92, but not visible in Figs. 2 and 4 since it is obscured by-the housing 60.
  • the distributing valve body 64, and the limiting valve assemblies 78 and 79 are shown in Fig. 3 in the assembled conditions and as accommodated in the respective bores 62, 61 and 63. It may be seen that the sealing elements or rings 86 ad 88 are arranged at the opposite axial sides of the annular element 90 ⁇ in the first version and that the sealing element or ring 88 is arranged at the same axial side of the annular element as the guiding portion 81 in both versions. It may also-be seen that, because of its hexagonal cross-section, the guiding portion 81 is in contact with, and thus is guided by, the - surface bounding the bore 61 or 63, as shown in connection with the limiting valve assembly 78.
  • gaps 110 exist between the regions of contact of the guiding portion 81 with the surface bounding the respective bore 61 or 63, these gaps 110 providing for communication between the spaces accommodating the helical springs 89 and those accommodating the sealing element 88 in the respective bores 61 or 63.
  • the guiding portion 81 has been shown to have a hexagonal cress-section, it will be appreciated that the same combination of guiding and bypass functions could also be achieved by giving the bores 61 and 63 and the guiding portions 81 other non-complementary cross-sections with multiple contact areas therebetween.
  • each of the annular elements 90 has a central passage 93 through which the stem portion 82 of the respective limiting valve body 80 passes with clearance.
  • the central passage 93 has a substantially constant of diameter over its entire axial length.
  • the central passage 93 has a larger-diameter first section 71 closer to, and a smaller-diameter second section 112 more remote from, the guiding portion 81 of the respective valve member 80 as considered in the assembled condition of the respective valve assembly 78 or 79.
  • the first section 111 is so dimensioned as to permit virtually unimpeded flow of air past the stem position 82.
  • the second section l12 is so dimensioned relative to the stem portion 82 as to cause a throttling action in the clearance between the stem portion 82 and the surface bounding the second passage 112.
  • the latter clearance is in the order of 1/10000 of an inch.
  • the annular element 80 further has a substantially radially extending passage 94 which communicates the central passage 93 (intermediate the sections 111 and 112 in the second version) with a respective passage 95 provided in the housing 60 and opening into an actuating space 96 or 97 which is delimited in the bore 62 by the respective shell 41 or 42 and the respective terminal collar 70 or 71 that is close to it.
  • the housing 60 also has a feeding duct 98 which is connected to the aformentioned feeding connector and opens into the bore 62 substantially centrally thereof, and a branched or bifurcated discharge duct 99 which opens into the bore 62 at locations at least axially spaced by a predetermined distance from and at opposite axial sides of the feeding duct 98.
  • the discharge duct 99 leads to the discharge nipple 92 mentioned above.
  • the housing 60 further has two discharge channels 100 each of which communicates, at one of its ends, with a space 101 of the respective bore 61 or 63 next to the respective annular element 90 and, at its other end, in a manner which is not shown in the drawing, with the discharge nipple 92. Furthermore, the housing 60 has two feeding channels 102 each of which communicates, at its one end, with a space 103 of the respective bore 61 or 63 that accommodates the helical spring 89 and, at its other end, in a manner which is also not illustrated, with the aforementioned feeding nipple or connector. The channels 100 and 102 are covered, in a sealing manner, by the respective shells 41 and 42. Finally, the housing 60 also has supply and relief ducts 104 and 105 which open into the bore 62 at locations situated axially spaced from and between the locations at which the feeding duct 98 and the discharge duct 99 open into the bore 62.
  • the respective shells 41 and 42 are provided'with - orifices 106 through which the supply and relief ducts 104 and 105 are in communication with the respective chambers 47 and 48 of the pumping units 3 and 4.
  • the shells 41 and 42 further have openings 107 through which the stem portions 82 of the respective valve members 80 pass into the respective chambers 47 and 48, being sealed in the openings 107 by respective self lubricatinc seals 108 of a conventional construction.
  • the housing 60 is advantageously made of aluminum and is provided, at least all over the surface bounding the bore 62, with a hard anodized coating layer 109.
  • the valve member or spool 64 is made, either in its entirety, or at least at its portion that comes into contact with the layer 109, of a materiel that needs no lubrication or is self-lubricating. Many such self-lubricating materials are known, but particularly good results were obtained with the spool 64 being made of polytetrafluoroethylene mixed with a mica filler. However, since this material has a tendency to swell under certain operating conditions, it was attempted to make the spool 64 with a core of a metallic material and with a cladding layer of the polytetrafluoroethylene.
  • the positions of the various components of the control arrangement 2 as illustrated in Fig. 3 are those which such components assume at the time of reversal from movement of the shaft 51 (see Fi g. 1) in the rightward direction to the movement in the leftward direction, and more particularly at the beginning of. the leftward movement.
  • the valve member 80 of the limiting valve 79 is in its rightmost position, being maintained therein by the action of the spring- 89 and the difference between the pressures acting on the valve member 80 in the opposite axiel directions.
  • This means that the seal 88 is in a sealing contact with both the annular element 90 and the guiding portion 81 of the limiting valve assembly 79, so that it interrupts communication between the gaps 110 and the central passage 93.
  • the sealing element 87 is spaced from the annular element 90, which means that an uninterrupted path is established between the chamber 97 through the duct 95, the radial passage 94, the central passage 93, the space 101 and the channel 100, ultimately with the discharge nipple 92.
  • the pressure then prevailing in the chamber 97 will be substantially equal to the ambient pressure, while the pressure in the space 103 is superatmospheric, resulting in the aforementioned pressure difference.
  • Figs. 3 and 5 also show that the mounting element 53, of which only a fragment is shown, has previously, during its-rightward movement, contacted the stem portion 82 of the valve member 80 of the limiting valve assembly 78 and depressed it, so that the entire limiting valve assembly 78 has been shifted in the rightward direction from its position into which it is urged by the spring 89.
  • This movement in the rightward direction eventually resulted in the illustrated situation where in the first version the sealing element 87, aided by the resilient action of the spring washer 85, seals the interfaces between the annular element 90, the stem portion 82 and the annular washer 86, thereby interrupting the communication between the passage 93 and tne space 101, the channel 100 and ultimately the discharge nipple 92.
  • any subsequent reduction of the pressure in the space 96 does not have any influence on the position of the spool 64.
  • the clearance in the larger-diameter section 85 of the passage 93 will have to be sufficient to not only compensate for the aforementioned leakage through the section 86, but also to permit flow of a sufficient excess amount of the compressed fluid into the space 96 to fill the same as tne spool 64 recedes during its rightward shift.
  • the above-mentioned rightward shift of the spool 64 has also interrupted the previously existing communication between the chamber 48 through the orifice 106, the duct 105, the channel 66 and the duct 98 ultimately with the feeding nipple.
  • the rightward shift of the spool 64 has established communication between the chamber 48 through the orifice 106, the duct 105, the channel 66 and the right-hand branch of the duct 99 ultimately with the discharge nipple 92.
  • This leftward movement which also involves the leftward movement of the mounting element 53, will be accompanied by concurrent leftward movement of the valve member 80 of the limiting valve assembly 78 under the action of the associated helical spring 89, until communication of the space 96 with the channel 102 is interrupted with attendant cessation of supply of the pressurized fluid into the passages 93 and 94, the duct 95 and the space 96.
  • the communication of the space 96 with the channel 100 is established at the same time whereby the pressure in the space 96 is relieved.
  • the clearance in the passage section 112 continues to permit the throttled flow of the fluid therethrough into the space 101 and the channel 100, whereby the pressure in the space 96 is relieved.
  • the spool 64 will remain in its then assumed position since the pressure in the space 97 is substantially the same as that.in the space 96 or, at least initially, lower.
  • the spool 64 remains in this position until the mounting element 55 of the movable wall 56 contacts the stem portion 82 of the valve member 80 of the limiting valve assembly 79 and depresses the same to the extent necessary to interrupt the communication of the space 97 with the channel 100 and establish communication of the chamber 97 with the channel 102.
  • the arrangement of the present invention uses the separating rings 76 and 77 which are made of a relatively rigid synthetic plastic material which is also of the self-lubricating type.
  • a material particularly well suited for this purpose is polytetrafluoroethylene filled with graphite.
  • these separating rings 76 and 77 slide along the inner surface of the coating layer 109, they will gradually wear off to a slight extent, which will deposit a layer cf polytetrafluoroethylene and/or graphite on the internal surface of the coating layer 109.
  • This deposited layer including the ingredients which have become dissociated from the spool 64 and/or the separating rings 7 6 and 77 will act as a lubricant and eliminate or at least slow down the further wear of the separating rings 76 and 77.
  • the deposited material will fill any crevices cr depressions in the herd anodized coating layer 109, thus presenting a highly smooth slicing surface to the spool 64 and the separating rings 76 and 77.
  • the back-up resilient expansion rings 74 and 75 urge the separating rings 76 and 77, respectively, in the radially outward direction into sliding contact with the internal surface of the coating layer 109. This introduces a certain amount'of drag or hesitation into the movement of the spool 64 so that, even if the spool 64 is subject to vibrations, such as may occur during the operation of the pump, it will not accidentally shift out of its respective end position toward the other end position.
  • the separating rings 76 and 77 are split to be able to radially outwardly expand in response to the urging of the resilient expansion rings 74 and 75.
  • This split introduces a discontinuity into the separating ring 76 or 77, through which fluid could flow between the channel 65 and the space 96 or the channel 66 and the space 97.
  • experience has shown that such leakages are negligible and do not adversely effect the operation of the control arrangement 5. Additional amounts of the compressed gaseous medium could flow past the separating rings 76 and 77 at the interfaces thereof with the delimiting collars 68 or 69 and the terminal collars 70 and 71.
  • the presence and sealing effect of the separating rings 76 and 77 prevent more serious leakages of the pressurized air through the interfaces between the spool 64 and the coating layer 109, which would otherwise result in undesired pressure buildups or reductions; with attendant reduction in or loss of operating reliability.
  • the guiding portions 81 of the valve members 80 are preferably of such a material and have such a shape as also to need no lubrication. This means that the limiting valve assemblies 78 and 79 will not have to be lubricated either, so that the pressurized air which is used to operate the control arrangement 5 need not have to have any oil droplets entrained therein. This is a pronounced advantage as compared to conventional valve or pump arrangements, in that any dust or other contaminants which may be present in the pressurized air will not be caused to adhere to the various components of the control arrangement 5 by the action of the entrained oil or similar lubricant.
  • the hexagonal cross-section of the guiding portions 81, with the attendant limited contact between the respective guiding portion 81 and the surface bounding the bore 61 or 63, is particularly useful in eliminating the need for lubrication.
  • the outlet nipple connector 92 is shown to be constructed as a silencer, so that it can be used in an ambient environment with discharge of the spent air into the ambient atmosphere.
  • a hose or a similar conduit to the connector 92 and to have such a hose lead to the exterior of the liquid medium in which the pump 1 is submersed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Saccharide Compounds (AREA)
EP84201842A 1983-12-23 1984-12-12 Pompe à diaphragmes actionnée par l'air et soupape pour cette pompe Withdrawn EP0147889A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US06/564,947 US4555222A (en) 1983-12-23 1983-12-23 Air-operated diaphragm pump and a valve arrangement therefor
US06/564,944 US4494574A (en) 1983-12-23 1983-12-23 Valve arrangement for an air-operated diaphragm pump
US564944 1983-12-23
US564947 1983-12-23

Publications (1)

Publication Number Publication Date
EP0147889A1 true EP0147889A1 (fr) 1985-07-10

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ID=27073697

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84201842A Withdrawn EP0147889A1 (fr) 1983-12-23 1984-12-12 Pompe à diaphragmes actionnée par l'air et soupape pour cette pompe

Country Status (3)

Country Link
EP (1) EP0147889A1 (fr)
CA (1) CA1224970A (fr)
NO (1) NO844999L (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2708050A1 (fr) * 1993-07-20 1995-01-27 Graco Inc Appareil de pompage à double membrane ayant un actionneur à ventouse à deux étapes.

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107889725A (zh) * 2017-11-27 2018-04-10 王建锋 多节自动伸缩喷灌出水口

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2471285A (en) * 1944-11-08 1949-05-24 David Y Rice Valve
FR2314414A1 (fr) * 1975-06-12 1977-01-07 Frank Roger Distributeur de fluide gazeux sous pression, notamment pour circuits logiques pneumatiques
FR2341799A1 (fr) * 1976-02-17 1977-09-16 Festo Maschf Stoll G Ajutage a pression dynamique
US4245670A (en) * 1978-11-06 1981-01-20 Robertshaw Controls Company Reversing valve construction and piston head assembly therefor and methods of making the same
GB2061768A (en) * 1979-10-22 1981-05-20 Devilbiss Co Spray guns
US4381180A (en) * 1981-07-13 1983-04-26 Sell John R Double diaphragm pump with controlling slide valve and adjustable stroke
FR2518660A1 (fr) * 1981-12-23 1983-06-24 Champion Spark Plug Co Pompe a diaphragmes
US4406596A (en) * 1981-03-28 1983-09-27 Dirk Budde Compressed air driven double diaphragm pump

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2471285A (en) * 1944-11-08 1949-05-24 David Y Rice Valve
FR2314414A1 (fr) * 1975-06-12 1977-01-07 Frank Roger Distributeur de fluide gazeux sous pression, notamment pour circuits logiques pneumatiques
FR2341799A1 (fr) * 1976-02-17 1977-09-16 Festo Maschf Stoll G Ajutage a pression dynamique
US4245670A (en) * 1978-11-06 1981-01-20 Robertshaw Controls Company Reversing valve construction and piston head assembly therefor and methods of making the same
GB2061768A (en) * 1979-10-22 1981-05-20 Devilbiss Co Spray guns
US4406596A (en) * 1981-03-28 1983-09-27 Dirk Budde Compressed air driven double diaphragm pump
US4381180A (en) * 1981-07-13 1983-04-26 Sell John R Double diaphragm pump with controlling slide valve and adjustable stroke
FR2518660A1 (fr) * 1981-12-23 1983-06-24 Champion Spark Plug Co Pompe a diaphragmes

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2708050A1 (fr) * 1993-07-20 1995-01-27 Graco Inc Appareil de pompage à double membrane ayant un actionneur à ventouse à deux étapes.
GB2280479A (en) * 1993-07-20 1995-02-01 Graco Inc Pilot and main valve controlled double-diaphragm pump
GB2280479B (en) * 1993-07-20 1996-12-04 Graco Inc A two-stage air valve actuator for a double-diaphragm pump

Also Published As

Publication number Publication date
NO844999L (no) 1985-06-24
CA1224970A (fr) 1987-08-04

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