EP0449686B1 - Equipage mobile télescopique d'entrainement d'une pompe alternative - Google Patents

Equipage mobile télescopique d'entrainement d'une pompe alternative Download PDF

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Publication number
EP0449686B1
EP0449686B1 EP91400633A EP91400633A EP0449686B1 EP 0449686 B1 EP0449686 B1 EP 0449686B1 EP 91400633 A EP91400633 A EP 91400633A EP 91400633 A EP91400633 A EP 91400633A EP 0449686 B1 EP0449686 B1 EP 0449686B1
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EP
European Patent Office
Prior art keywords
equipment according
moving equipment
piece
slider
pieces
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.)
Expired - Lifetime
Application number
EP91400633A
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German (de)
English (en)
French (fr)
Other versions
EP0449686A1 (fr
Inventor
Jean-Claude Degremont
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.)
Dosapro Milton Roy SA
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Dosapro Milton Roy SA
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Publication date
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Application filed by Dosapro Milton Roy SA filed Critical Dosapro Milton Roy SA
Priority to AT91400633T priority Critical patent/ATE97199T1/de
Publication of EP0449686A1 publication Critical patent/EP0449686A1/fr
Application granted granted Critical
Publication of EP0449686B1 publication Critical patent/EP0449686B1/fr
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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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/121—Lost-motion device in the driving mechanism

Definitions

  • diaphragm pumps in which the diaphragm is hydraulically actuated and those in which the diaphragm is mechanically actuated.
  • a reciprocating piston acts in a chamber which contains a determined volume of "motor" liquid, one of the walls of the chamber being formed by the membrane to be actuated.
  • the depression of the piston in this control chamber pushes the membrane back into the working chamber which sees its volume decrease. This is the pump discharge phase.
  • the piston creates a suction of the control liquid which drives the membrane backwards.
  • the volume of the working chamber increases. This is the suction phase of the pump.
  • the suction height in this type of pump is limited by the cavitation of the working liquid.
  • this diaphragm is coupled to a mobile assembly driven by an alternating movement.
  • a mobile assembly driven by an alternating movement.
  • the moving assembly of the crank-rod type or rather a slide coupled to an eccentric.
  • the eccentric acts like a cam which pushes the moving part (pump delivery phase), the return being ensured elastically.
  • the mobile assembly is coupled to the eccentric by means of a coupling nut which provides the return drive.
  • the adjustment of the flow rate of these diaphragm pumps consists of acting on two operating parameters: the amplitude of the stroke and the cadence. In practice, one acts on the rate by allowing an adjustment of the speed of the eccentric drive motor. Regarding the adjustment of the stroke amplitude, the mechanisms depend on the technology of the pumps. Thus for hydraulically controlled pumps, it is possible to adjust, for a constant amplitude of stroke of the piston, the quantity of displaced control liquid. To do this, the control chamber is in part contained by a cavity in the piston which has lateral orifices for communication with the reservoir, these orifices being discovered over an adjustable part of the stroke around the rear dead center of the piston (at the end of the suction phase). To illustrate this technique, document EP 148 691 will be cited.
  • the stroke adjustment is generally carried out by limiting the return amplitude of the slide under the effect of the return spring by means of an adjustable stop, as for example documents US-A- 4,167,896 or GB-A- 2,044,895.
  • the present invention is a response adapted to the state of the market, that is to say a mechanism for adjusting the flow rate of a pump with mechanical actuation having the same advantages as a pump with hydraulic control with regard to the ease of adjustment and conservation of pumping characteristics whatever the flow rate.
  • a movable equipment for driving an alternative pump with adjustable stroke comprising a slide mounted sliding in a fixed guide, cooperating by one of its ends with an eccentric motor device, whose eccentricity defines the maximum amplitude of the stroke of the slide in the guide, and coupled by its other end to the active pumping member which can be either a membrane, or by extension a rigid piston.
  • the active pumping member which can be either a membrane, or by extension a rigid piston.
  • the slide is telescopic with two sliding parts, one relative to the other, parallel to the guide, one drive being coupled to the eccentric, and the other driven being coupled to the membrane, the two parts being, in the retracted state of the slide, held in abutment against each other by means of a coupling member developing a determined holding force while the driven piece of the slide has a cooperating stop member with an adjustable stop along the guide, hampering the travel of this driven part to limit the amplitude to a fraction of the maximum amplitude generated by the rotation of the eccentric, and opposing the holding effort an appropriate effort , leading to the extension of the slide.
  • the coupling member comprises at least one movable element for locking the two parts which cooperates with a cam surface carried by one of the parts tending to obliterate the movable element radially in a housing provided in the other part, against an elastic return member which defines the predetermined effort to overcome to make possible the extension of the slide.
  • This embodiment has two advantages: the first lies in the fact that the predetermined force to be overcome defines the suction height of the pump which remains constant regardless of the adjustment of the stroke. The second results from the erasure of the locking member which no longer exerts any significant residual force between the driving part and the driven part of the slide, so that the stop of the driven part is not subjected more constraint.
  • the end of the driving part of the slide opposite the eccentric has a bore in which is slidably mounted the end of the driven part opposite the membrane, the movable locking element being constituted by a ball housed in a recess formed radially in one of the parts subjected to the effect of an elastic member tending to extract it from the recess, the cam surface being constituted by the side of a groove formed in the other part .
  • the elastic element in a first variant the elastic element is arranged in the radial recess, and in a second variant the elastic element consists of a spring housed axially in the driven part, interposed between a fixed support of the latter and a cam, sliding axially in the driven part, which bears under the effect of the spring on the ball by a diverging cam surface.
  • the cam or the driven part comprises a member for adjusting the spring setting.
  • the elastic member may be an elastic strip disposed in an external groove of the driving part into which the recess opens.
  • the coupling member comprises a claw integral with one of the parts, having a plurality of teeth elastically deformable in a radial direction and whose free ends, which form the element movable locking, are engaged in a groove of the other part, in the retracted state of the slide.
  • the coupling member comprises a locking pawl pivoting on the driven part and engaged behind a stop of the driving part when the slide is retracted, under the effect of an elastic member, this pawl being integral with an operating lever whose free end constitutes the stop member of the driven part pivoting against the effect of the elastic member in the direction of release of the pawl when in contact with the adjustable stop along the guide.
  • the coupling member is constituted by a calibrated elastic member disposed between the two parts of the slide and the effect of which tends to keep the slide in its retracted position under a determined force.
  • the elastic member may consist of an elastomer part, in each of the embodiments except perhaps the case of the external elastic strip presented above.
  • a diaphragm pump is shown diagrammatically in FIG. 1 and comprises a pumping head 1 in which a diaphragm 2 defines a pumping chamber 3 which is connected to a suction pipe 4 and a delivery pipe 5 through one-way valves 6 and 7.
  • the diaphragm 2 of this pump is coupled to one of the ends of a slide 8, the other end of which cooperates with an eccentric 9 for driving by means of a sliding pad 10 acting sometimes on the face 11 of the slide, sometimes on its face 12 to transform the continuous rotary movement A of the eccentric 9 into an alternative rectilinear movement B of the slide.
  • the slide 8 is guided in its front part by a fixed guide 13 belonging to the pump frame and is supported at its rear part by the axis 10 a of rotation of the eccentric by means of the edges of the light 14 traversed by this axis.
  • the section of the slide in the guide is circular, or of any shape suitable for simple machining of the guide and the slide.
  • the slide 8 is made in two parts 15 and 16 so as to be telescopic.
  • the part 15 which is coupled to the membrane 2 has one end 17 slidingly mounted, parallel to the guide 13, in a bore 18 of the part 16 cooperating with the eccentric 9,10.
  • the front end 18 a of the part 16 rests on a shoulder 17 a of the part 15, the part 17 then being completely housed in the bore 18.
  • the two parts 15 and 16 are linked by a coupling device whose function will be explained with reference to its schematic representation 19 of FIGS. 1 to 3.
  • This device comprises two balls 20 and 21 housed in a diametrical recess 22 of the part 17 of the part 15. These two balls are urged by an elastic member 23 tending to push them out of the recess.
  • the bore 18 has a groove 24 arranged so that, when the slide is retracted, the balls 20 and 21, under the effect of the elastic member 23, penetrate at least partially into the groove 24 s' pressing on the blank 25 of this groove which is turned away from the front face 18 a of the part 16.
  • This flank 25 plays the role of a cam surface (it can for this purpose be inclined) which receives the effort developed by the resilient member 23 and transmitted by the balls and which transmits to the part 16 an axial component tending to keep the support piece on the shoulder 17a of the piece 15.
  • the intensity of this effort depends on the effort generated by the elastic member 23 and on the geometry of the ball contact surfaces 20, 21 / side 25 of the groove 24. It is therefore understood that as long as the effort tends to separate the two parts 15 and 16 is less than this coupling force, the slide behaves as if it were a single piece. On the other hand, if this force is greater than the coupling force, the balls 20 and 21 are erased by the cam side 25 of the groove 24 and the two parts 15 and 16 slide relative to each other . It will be noted that the only force opposing this sliding is practically independent of the force developed by the spring 23 since it comes down to the sole friction forces of the balls on the wall of the bore 18.
  • the part 15, called the driven part has a stop member 26, shown here in the form of a radial finger, which passes through the fixed guide 13 through a slot 27 whose length measured axially, is at least equal to the maximum amplitude of the stroke of the slide 8, that is to say 2 e if e is the eccentricity of the cam 9 relative to the rotation shaft 10 a .
  • the fixed guide carries a stop 28 adjustable in position relative to the light, in the sliding direction.
  • This stop 28 is here produced in the form of an eccentric disc by relative to a pivot axis 29 and angularly indexable about this axis by means not described and known in themselves, which may include a manual adjustment button.
  • the stop 28 more or less covers the light 27 and more or less limits the amplitude of the movement of the finger 26 in this light.
  • This adjustable stop constitutes the pump flow adjustment member, all other things being equal.
  • the stop 28 is in a position revealing a length of light 27 sufficient for the finger 26 to be able to travel a length of it 2 e .
  • the rotation of the eccentric cam 9 generates an alternating movement of the slide 8. Its forward movement (the left of FIG. 1) constitutes the pump delivery phase. Its backward travel (the right in Figure 1) is the suction phase of the pump.
  • the driving force developed by the cam is transmitted to the membrane by the slide 8 the two parts 16 and 15 resting one upon the other by their surfaces 18a, 17a.
  • the engine force is transmitted to the membrane through the coupling mechanism 19, that is to say by the latch of the part 15 on the part 16 by means of the balls.
  • the suction force corresponds to the suction column which one wishes to be able to raise with the pump and this can easily be supported by the coupling device 19 (appropriate choice of the spring 23 and its calibration for determined ball dimensions).
  • the moving assembly therefore behaves like a rigid connecting rod assembly.
  • FIG. 3 illustrates the return of the part 16 in the direction of the part 15 which it approaches by its surface 18 a on the surface 17 a of the shoulder, since it pushes in the direction of the neutral point before the pump to drive back the quantity of product previously aspirated.
  • the groove 24 allows the balls 20 and 21 to return to their original place and the two parts 15 and 16 are again coupled.
  • FIGS. 4A and 4B are sectional views of a first practical embodiment of the invention, in the state of the mobile assembly respectively in FIGS. 1 and 2. These figures show some of the elements already described with the same references.
  • the part 15 is here tubular with an internal shoulder 30, to receive a rod 31 having an end 32 in the manner of a valve which forms a cam surface cooperating with the balls 20 and 21.
  • a spring 33 is interposed between the shoulder 30 and nut 34 integral with the rod 31. Its effect tends to apply the part 32 against the balls 20 and 21 in order to extract them radially from their housing 22.
  • the nut 34 makes it possible to adjust the calibration of the spring 33, therefore the coupling force parts 15 and 16 and therefore the suction power of the pump.
  • this disengageable coupling constitutes a protection security for the pump mechanism.
  • the resistant force can increase until overcoming the coupling force which will yield. This will have avoided subjecting the membrane to too great a stress which could lead to its premature rupture.
  • Certain shaped membranes are in fact more resistant to the discharge force than to the suction force.
  • FIGS. 5A and 5B each represent a variant of the preceding figures in the same states of the moving assembly.
  • the part 15 is tubular, the bore being blind on the side of the balls 20 and 21.
  • the balls may be of a number greater than 2 and preferably three in number, housed in bores radials of the part 15 offset by 120 ° from each other.
  • the bore 35 of the part 15 receives a sliding plunger which can have either the shape of a needle 36 or that of a ball 37 (each of these elements being half shown in the figures).
  • a spring 38 is compressed behind this needle 36 or this ball 37, to apply them against the balls 20, 21 in order to force towards the outside of the part 15.
  • a threaded plug 39 in the bore 35 serves to adjust the calibration of the spring 38.
  • FIG. 10 Another embodiment of this variant is illustrated in FIG. 10 where the spring 38 is constituted by a elastomer block 40 compressed behind the ball 37 by the threaded plug 39.
  • FIGS. 6A and 6B apart from certain elements already described with the same references, there is shown a reverse arrangement of the preceding ones as regards the place of the balls.
  • These 41 are placed in the housings 42 of the part 16 and are forced to project towards the inside of the bore 18 by external elastic strips 43 housed in a groove 44 outside of the part 16 so as to be able to deform without being hindered by the guide 13.
  • the part 17 of the part 15 has for its part a groove 45 for partially accommodating the balls 41 and resting on them by its side 46 facing the shoulder 17 a .
  • the elastically deformable strip or strips 43 generate the coupling force of the two parts 15 and 16 for the same reasons as those given above.
  • FIG. 6B is an image of the elastic deformation of these strips when the balls 41 are forced into their housing 42 after the coupling of the parts 15 and 16 has been disengaged.
  • the coupling device shown in FIGS. 7A and 7B is a kind of elastic clamp having a plurality of elastically deformable teeth 47 (produced for example by slitting a cylindrical sleeve) integral with the part 15.
  • the ends 47 a of these teeth are engaged in the groove 24 of the part 16, one of the flanks 25 of which forms a cam surface for lifting the end 47 a of these teeth when the connection is disengaged.
  • the teeth can be replaced by a cylindrical sleeve with an external bead capable of elastically constricting.
  • FIG. 8A and 8B Another embodiment of the invention is shown in Figures 8A and 8B.
  • the disengageable connection of the two parts is ensured here by a pawl 50 pivoting about an axis 51 carried by the part 15.
  • the front surface 18a of this member 16 bears on the end 15 is drawn to the part 15 and the pawl 50 is pivoted in a slot 52 of the workpiece 15.
  • the end 53 of the pawl can engage in the groove 24 behind its side 25 of the part 16.
  • This engagement is forced by an elastic member 54 which exerts its force on a lever 55 integral with the pawl and pivoting with it around the axis 51.
  • the end 56 of this lever crosses the guide 13 through the light 27 to cooperate with the stop, the lever 55 rocks around the axis 51 and lifts the end 53 which comes out of the groove 24 and releases the connection of the parts 15 and 16.
  • FIGS. 9A and 9B a last embodiment of the invention is shown.
  • the part 17 of the part 15 is of smaller diameter than that of the bore 18 of the part 16.
  • the annular space thus existing makes it possible to accommodate a spring 57 compressed between a shoulder 58 carried by the end of the part 17 and a shoulder 59 provided at the inlet of the bore 18.
  • parts 15 and 16 can move relative to each other ( Figure 9B). This solution is only applicable for pumps with low suction head so that the coupling force remains low.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Vehicle Body Suspensions (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Fittings On The Vehicle Exterior For Carrying Loads, And Devices For Holding Or Mounting Articles (AREA)
EP91400633A 1990-03-29 1991-03-07 Equipage mobile télescopique d'entrainement d'une pompe alternative Expired - Lifetime EP0449686B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91400633T ATE97199T1 (de) 1990-03-29 1991-03-07 Teleskopische bewegliche ausruestung zum antrieb einer verdraengungspumpe.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9004020A FR2660374B1 (fr) 1990-03-29 1990-03-29 Equipage mobile telescopique d'entrainement d'une pompe alternative.
FR9004020 1990-03-29

Publications (2)

Publication Number Publication Date
EP0449686A1 EP0449686A1 (fr) 1991-10-02
EP0449686B1 true EP0449686B1 (fr) 1993-11-10

Family

ID=9395239

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91400633A Expired - Lifetime EP0449686B1 (fr) 1990-03-29 1991-03-07 Equipage mobile télescopique d'entrainement d'une pompe alternative

Country Status (8)

Country Link
US (1) US5074763A (ja)
EP (1) EP0449686B1 (ja)
JP (1) JPH0758067B2 (ja)
AT (1) ATE97199T1 (ja)
CA (1) CA2038805A1 (ja)
DE (1) DE69100609T2 (ja)
ES (1) ES2047384T3 (ja)
FR (1) FR2660374B1 (ja)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2682720A1 (fr) * 1991-10-17 1993-04-23 Pcm Pompes Procede de pompage a debit reglable continuement entre une valeur nulle et une valeur maximale et pompe a debit reglable mettant en óoeuvre ce procede.
JP3373558B2 (ja) * 1992-04-23 2003-02-04 松下電工株式会社 小型ポンプ装置
US5437218A (en) * 1994-04-04 1995-08-01 Pcm Pompes Diaphragm pump having variable displacement
US5957669A (en) * 1995-06-15 1999-09-28 United States Filter Corporation Diaphragm pump including improved drive mechanism and pump head
US6354819B1 (en) 1996-06-14 2002-03-12 United States Filter Corporation Diaphragm pump including improved drive mechanism and pump head
US6082979A (en) * 1997-06-23 2000-07-04 Sealand Technology, Inc. Air pump for vacuum toilet systems
FR2966525B1 (fr) * 2010-10-22 2012-11-16 Milton Roy Europe Pompe a membrane a forte capacite d'aspiration
CN102937089B (zh) * 2012-11-19 2016-01-20 浙江爱力浦泵业有限公司 一种机械隔膜计量泵膜片传动机构
US9709050B2 (en) * 2014-01-07 2017-07-18 Rocky Research Solution pump system
EP3716892A1 (en) * 2017-11-28 2020-10-07 Koninklijke Philips N.V. Oral cleaning device with variable fluid pressurization
CN110454350A (zh) * 2019-09-17 2019-11-15 郑州三惠机械设备有限公司 一种调色机的双级流量色浆供应装置

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2929253A (en) * 1957-12-18 1960-03-22 Baldelli Gaetano Device for adjusting from outside, continuously and during its operation, the capacity of a plunger pump
US3164024A (en) * 1960-10-21 1965-01-05 Wallace & Tiernan Inc Drive mechanism and diaphragm pump employing same
SE7413016L (sv) * 1974-10-16 1976-04-20 Piab Ab Pump med fram- och atergaende pumporgan
US4167896A (en) * 1977-08-11 1979-09-18 Gustafson, Inc. Pump for auger treater
FR2568530B1 (fr) * 1984-08-03 1989-01-27 Marchal Equip Auto Dispositif de lave-glace, comprenant une pompe associee a au moins un essuie-glace

Also Published As

Publication number Publication date
FR2660374A1 (fr) 1991-10-04
FR2660374B1 (fr) 1992-07-03
DE69100609T2 (de) 1994-06-01
ES2047384T3 (es) 1994-02-16
JPH04224287A (ja) 1992-08-13
CA2038805A1 (fr) 1991-09-30
US5074763A (en) 1991-12-24
EP0449686A1 (fr) 1991-10-02
JPH0758067B2 (ja) 1995-06-21
DE69100609D1 (de) 1993-12-16
ATE97199T1 (de) 1993-11-15

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