EP0449686A1 - Telescopic mobile equipment for driving a reciprocating pump - Google Patents

Telescopic mobile equipment for driving a reciprocating pump Download PDF

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Publication number
EP0449686A1
EP0449686A1 EP91400633A EP91400633A EP0449686A1 EP 0449686 A1 EP0449686 A1 EP 0449686A1 EP 91400633 A EP91400633 A EP 91400633A EP 91400633 A EP91400633 A EP 91400633A EP 0449686 A1 EP0449686 A1 EP 0449686A1
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EP
European Patent Office
Prior art keywords
slide
assembly according
movable assembly
movable
parts
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EP91400633A
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German (de)
French (fr)
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EP0449686B1 (en
Inventor
Jean-Claude Degremont
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Dosapro Milton Roy SA
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Dosapro Milton Roy SA
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    • 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 delivery phase of the pump.
  • the piston In its reverse stroke, 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 effort to maintain an effort to less equal, 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 divergent 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 with regard to 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.

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  • 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)

Abstract

The slide 8 of the moving element of the pump is in two telescopic sections 15 and 16, the one (15) coupled to the diaphragm, the other (16) coupled to the eccentric cam and connected together by a disengageable connecting device (19) when the flow regulating stop (28) obstructs the travel of the part (15). <IMAGE>

Description

Il existe deux catégories de pompes à membranes : les pompes dans lesquelles la membrane est actionnée hydrauliquement et celles dans lesquelles la membrane est actionnée mécaniquement. Dans les pompes à actionnement hydraulique, un piston animé d'un mouvement alternatif agit dans une chambre qui contient un volume déterminé de liquide "moteur", l'une des parois de la chambre étant constituée par la membrane à actionner. L'enfoncement du piston dans cette chambre de commande repousse la membrane dans la chambre de travail qui voit son volume diminuer. C'est la phase de refoulement de la pompe. Dans sa course inverse, le piston crée une aspiration du liquide de commande qui entraîne vers l'arrière la membrane. Le volume de la chambre de travail augmente. C'est la phase d'aspiration de la pompe. La hauteur d'aspiration est dans ce type de pompe limitée par la cavitation du liquide de travail.There are two categories of diaphragm pumps: pumps in which the diaphragm is hydraulically actuated and those in which the diaphragm is mechanically actuated. In hydraulically actuated pumps, 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 delivery phase of the pump. In its reverse stroke, 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.

Dans le cas d'une pompe avec membrane actionnée mécaniquement, cette membrane est attelée à un équipage mobile animé d'un mouvement alternatif. Il existe plusieurs mécanismes moteurs pour l'équipage mobile, du type bielle manivelle ou plutôt coulisseau attelé à un excentrique. Pour certains d'entre eux, l'excentrique agit comme une came qui pousse l'équipage mobile (phase de refoulement de la pompe) le retour étant assuré élastiquement. Pour d'autres, l'équipage mobile est attelé à l'excentrique par l'intermédiaire d'une noix d'attelage qui assure l'entraînement aller-retour.In the case of a pump with a mechanically actuated diaphragm, this diaphragm is coupled to a mobile assembly driven by an alternating movement. There are several motor mechanisms for the moving assembly, of the crank-rod type or rather a slide coupled to an eccentric. For some of them, the eccentric acts like a cam which pushes the moving part (pump delivery phase), the return being ensured elastically. For others, the mobile assembly is coupled to the eccentric by means of a coupling nut which provides the return drive.

Le réglage du débit de ces pompes à membrane consiste à agir sur deux paramètres de fonctionnement : l'amplitude de la course et la cadence. Dans la pratique, on agit sur la cadence en permettant un réglage de la vitesse du moteur d'entraînement de l'excentrique. Pour ce qui concerne le réglage de l'amplitude de la course, les mécanismes dépendent de la technologie des pompes. Ainsi pour les pompes à commande hydraulique, on peut régler, pour une amplitude constante de course du piston, la quantité de liquide de commande déplacé. Pour ce faire la chambre de commande est en partie contenue par une cavité dans le piston qui comporte des orifices latéraux de communication avec le réservoir, ces orifices étant découverts sur une partie réglable de la course aux environs du point mort arrière du piston (à la fin de la phase d'aspiration). On citera pour illustrer cette technique le document EP 148 691.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.

Par ailleurs, pour les pompes à actionnement mécanique, le réglage de la course s'opère généralement en limitant l'amplitude de retour du coulisseau sous l'effet du ressort de rappel au moyen d'une butée réglable, comme cela apparaît par exemple des documents US-A- 4 167 896 ou GB-A- 2 044 895.Furthermore, for mechanically actuated pumps, 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.

Il n'existe pas de solution avantageuse pour le réglage de l'amplitude de la course lorsque l'aspiration est réalisée par entraînement positif de l'équipage mobile par l'excentrique.There is no advantageous solution for adjusting the amplitude of the stroke when the suction is carried out by positive drive of the mobile assembly by the eccentric.

Pour certains marchés, tels que le traitement des eaux de rejet, les pompes à actionnement hydraulique sont encore perçues comme un produit compliqué demandant une surveillance et un entretien coûteux. En outre, les utilisateurs craignent toujours une rupture de membrane qui peut conduire au mélange du liquide traité avec le fluide de commande (de l'huile) avec des conséquences importantes au plan de la pollution. Le remède à ce risque existe par la mise en place de double membranes avec dispositif de détection de rupture, ce qui, effectivement complique les appareils aux yeux d'utilisateurs habitués à du matériel plus simple.For some markets, such as waste water treatment, hydraulically actuated pumps are still seen as a complicated product requiring costly monitoring and maintenance. In addition, users still fear a rupture of the membrane which can lead to mixing of the treated liquid with the control fluid (oil) with significant consequences in terms of pollution. The remedy for this risk exists by the installation of double membranes with rupture detection device, which effectively complicates the devices in the eyes of users accustomed to simpler equipment.

La présente invention est une réponse adaptée à l'état du marché, c'est-à-dire un mécanisme de réglage du débit d'une pompe à actionnement mécanique présentant les mêmes avantages qu'une pompe à commande hydraulique en ce qui concerne la facilité de réglage et la conservation des caractéristiques de pompage quel que soit le débit.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 cet effet, elle a donc pour objet un équipage mobile d'entraînement d'une pompe alternative, à course réglable comprenant un coulisseau monté glissant dans un guide fixe, coopérant par l'une de ses extrémités avec un dispositif moteur à excentrique, dont l'excentricité définit l'amplitude maximale de la course du coulisseau dans le guide, et attelé par son autre extrémité à l'organe actif de pompage qui peut être soit une membrane, soit par extension un piston rigide. Dans ce qui suit on ne se réfèrera qu'aux pompes à membranes, mais l'invention s'applique à toutes les pompes alternatives quelle que soit la nature du piston attelé à l'équipage mobile.To this end, it therefore relates to 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. In what follows we will only refer to diaphragm pumps, but the invention applies to all alternative pumps regardless of the nature of the piston coupled to the moving element.

Selon l'invention le coulisseau est télescopique avec deux pièces coulissantes, l'une par rapport à l'autre, parallèlement au guide, l'une motrice étant attelée à l'excentrique, et l'autre entraînée étant attelée à la membrane, les deux pièces étant, dans l'état rétracté du coulisseau, maintenues en appui l'une contre l'autre au moyen d'un organe d'attelage développant un effort de maintien déterminé tandis que la pièce entraînée du coulisseau possède un organe de butée coopérant avec une butée réglable le long du guide, entravant la course de cette pièce entraînée pour en limiter l'amplitude à une fraction de l'amplitude maximale engendrée par la rotation de l'excentrique, et opposant à l'effort de maintien un effort au moins égal, conduisant à l'extension du coulisseau.According to the invention 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 effort to maintain an effort to less equal, leading to the extension of the slide.

Dans un premier mode de réalisation l'organe d'attelage comporte au moins un élément mobile de verrouillage des deux pièces qui coopère avec une surface de came portée par l'une des pièces tendant à effacer radialement l'élément mobile dans un logement prévu dans l'autre pièce, à l'encontre d'un organe élastique de rappel qui définit l'effort prédéterminé à vaincre pour rendre possible l'extension du coulisseau. Ce mode de réalisation présente deux avantages : le premier réside dans le fait que l'effort prédéterminé à vaincre définit la hauteur d'aspiration de la pompe qui reste constante quel que soit le règlage de la course. Le second résulte de l'effacement de l'organe de verrouillage qui n'exerce alors plus d'effort résiduel significatif entre la pièce motrice et la pièce entraînée du coulisseau, si bien que la butée d'arrêt de la pièce entraînée ne subit plus de contrainte.In a first embodiment, 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.

De manière préférée, l'extrémité de la pièce motrice du coulisseau opposée à l'excentrique comporte un alésage dans lequel est montée coulissante l'extrémité de la pièce entraînée opposée à la membrane, l'élément mobile de verrouillage étant constitué par une bille logée dans un évidement ménagé radialement dans l'une des pièces soumise à l'effet d'un organe élastique tendant à l'extraire de l'évidement, la surface de came étant constituée par le flanc d'une gorge ménagée dans l'autre pièce. Si l'évidement est prévu dans la pièce entraînée et la gorge dans la pièce motrice, dans une première variante l'élément élastique est disposédans l'évidement radial, et dans une seconde variante l'élément élastique est constitué par un ressort logé axialement dans la pièce entraînée, interposé entre un appui fixe de celle-ci et une came, coulissante axialement dans la pièce entraînée, qui s'appuie sous l'effet du ressort sur la bille par une surface de came divergente. Dans ce dernier cas, la came ou la pièce entraînée comporte un organe de réglage du tarage du ressort.Preferably, 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 . If the recess is provided in the driven part and the groove in the driving part, 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 divergent cam surface. In the latter case, the cam or the driven part comprises a member for adjusting the spring setting.

Si l'évidement est prévu dans la pièce motrice et la gorge dans la pièce entraînée, l'organe élastique peut être une lamelle élastique disposée dans une gorge extérieure de la pièce motrice dans laquelle débouche l'évidement.If the recess is provided in the driving part and the groove in the driven part, the elastic member may be an elastic strip disposed in an external groove of the driving part into which the recess opens.

Dans une autre forme de ce premier mode de réalisation, l'organe d'attelage comporte une griffe solidaire de l'une des pièces, possédant une pluralité de dents élastiquement déformables dans une direction radiale et dont les extrémités libres, qui forment l'élément mobile de verrouillage, sont engagées dans une gorge de l'autre pièce, à l'état rétracté du coulisseau.In another form of this first embodiment, 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.

Dans un second mode de réalisation, l'organe d'attelage comporte un cliquet de verrouillage pivotant sur la pièce entraînée et engagé derrière une butée de la pièce motrice lorsque le coulisseau est rétracté, sous l'effet d'un organe élastique, ce cliquet étant solidaire d'un levier de manoeuvre dont l'extrémité libre constitue l'organe de butée de la pièce entraînée pivotant à l'encontre de l'effet de l'organe élastique dans le sens du dégagement du cliquet lors de son contact avec la butée réglable le long du guide.In a second embodiment, 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.

Enfin dans un troisième mode de réalisation l'organe d'attelage est constitué par un organe élastique taré disposé entre les deux pièces du coulisseau et dont l'effet tend à maintenir le coulisseau dans sa position rétractée sous un effort déterminé.Finally, in a third embodiment, 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.

L'organe élastique peut être constitué par une pièce en élastomère, dans chacune des réalisations hormis peut-être le cas de la lamelle élastique extérieure présenté plus haut.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.

D'autres particularités et avantages de l'invention ressortiront de la description ci-après de différentes réalisations faite en référence aux dessins annexés dans lesquels :

  • les figures 1, 2 et 3 sont trois schémas illustrant les moyens généraux de l'invention vus en coupe le long du plan axial de symétrie d'une pompe à membrane, dans trois états particuliers de la course de l'équipage mobile,
  • les figures 4A et 4B représentent, vu en coupe, un premier mode de réalisation de l'invention dans deux états différents de l'équipage mobile,
  • la figure 4C illustre une variante d'un détail de ce premier mode de réalisation,
  • les figures 5A et 5B illustrent par des vues semblables, une variante de réalisation des figures 4A et 4B,
  • les figures 6A et 6B illustrent une autre variante de la réalisation de l'équipage mobile de l'invention,
  • les figures 7A et 7B sont des vues semblables aux précédentes d'une autre variante de réalisation,
  • les figures 8A et 8B représentent un second mode de réalisation de l'équipage mobile selon l'invention,
  • les figures 9A et 9B sont des vues d'un troisième mode de réalisation.
  • la figure 10 est un schéma d'une variante de détail.
Other features and advantages of the invention will emerge from the description below of various embodiments made with reference to the appended drawings in which:
  • FIGS. 1, 2 and 3 are three diagrams illustrating the general means of the invention seen in section along the axial plane of symmetry of a diaphragm pump, in three particular states of the stroke of the moving assembly,
  • FIGS. 4A and 4B represent, seen in section, a first embodiment of the invention in two different states of the moving assembly,
  • FIG. 4C illustrates a variant of a detail of this first embodiment,
  • FIGS. 5A and 5B illustrate by similar views, an alternative embodiment of FIGS. 4A and 4B,
  • FIGS. 6A and 6B illustrate another variant of the embodiment of the mobile assembly of the invention,
  • FIGS. 7A and 7B are views similar to the previous ones of another alternative embodiment,
  • FIGS. 8A and 8B represent a second embodiment of the mobile assembly according to the invention,
  • Figures 9A and 9B are views of a third embodiment.
  • Figure 10 is a diagram of a variant detail.

Une pompe à membrane est représentée schématiquement à la figure 1 et comprend une tête de pompage 1 dans laquelle une membrane 2 définit une chambre de pompage 3 qui est reliée à un conduit d'aspiration 4 et un conduit de refoulement 5 au travers de clapets unidirectionnels 6 et 7.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.

La membrane 2 de cette pompe est attelée à l'une des extrémités d'un coulisseau 8 dont l'autre extrémité coopère avec un excentrique 9 d'entraînement au moyen d'un patin glissant 10 agissant tantôt sur la face 11 du coulisseau, tantôt sur sa face 12 pour transformer le mouvement rotatif continu A de l'excentrique 9 en un mouvement rectiligne alternatif B du coulisseau.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.

Le coulisseau 8 est guidé dans sa partie avant par un guide fixe 13 appartenant au bâti de la pompe et est soutenu à sa partie arrière par l'axe 10a de rotation de l'excentrique au moyen des bords de la lumière 14 traversée par cet axe. La section du coulisseau dans le guide est circulaire, ou de toute forme appropriée à un usinage simple du guide et du coulisseau.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.

Le coulisseau 8 est réalisé en deux parties 15 et 16 de manière à être télescopique. Ainsi la pièce 15 qui est attelée à la membrane 2 comporte une extrémité 17 montée à coulissement,parallèlement au guide 13, dans un alésage 18 de la pièce 16 coopérant avec l'excentrique 9,10. En position rétractée du coulisseau l'extrémité frontale 18a de la pièce 16 repose sur un épaulement 17a de la pièce 15, la partie 17 étant alors complètement logée dans l'alésage 18.The slide 8 is made in two parts 15 and 16 so as to be telescopic. Thus 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. In the retracted position of the slide, 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.

Les deux pièces 15 et 16 sont liées par un dispositif d'attelage dont la fonction sera expliquée en regard de sa représentation schématique 19 des figures 1 à 3.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.

Ce dispositif comporte deux billes 20 et 21 logées dans un évidement diamétral 22 de la partie 17 de la pièce 15. Ces deux billes sont sollicitées par un organe élastique 23 tendant à les pousser vers l'extérieur de l'évidement. L'alésage 18 possède quant à lui une gorge 24 disposée de sorte que, quand le coulisseau est rétracté, les billes 20 et 21, sous l'effet de l'organe élastique 23, pénètrent au moins partiellement dans la gorge 24 en s'appuyant sur le flan 25 de cette gorge qui est tourné à l'opposé de la face frontale 18a de la pièce 16. Ce flanc 25 joue le rôle d'une surface de came (il peut être à cet effet incliné) qui reçoit l'effort développé par l'organe élastique 23 et transmis par les billes et qui en transmet à la pièce 16 une composante axiale tendant à maintenir cette pièce en appui sur l'épaulement 17a de la pièce 15.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.

L'intensité de cet effort dépend de l'effort engendré par l'organe élastique 23 et de la géométrie des surfaces de contact billes 20,21/flanc 25 de la gorge 24. On comprend donc que tant que l'effort tendant à séparer les deux pièces 15 et 16 est inférieur à cet effort d'attelage, le coulisseau se comporte comme s'il était monobloc. En revanche, si cet effort est supérieur à l'effort d'attelage, les billes 20 et 21 sont effacées par le flanc-came 25 de la gorge 24 et les deux parties 15 et 16 coulissent l'une par rapport à l'autre. On notera que le seul effort s'opposant à ce coulissement est pratiquement indépendant de l'effort développé par le ressort 23 puisqu'il se résume aux seules forces de frottement des billes sur la paroi de l'alésage 18.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.

La pièce 15, dite pièce entraînée, possède un organe de butée 26, représenté ici sous la forme d'un doigt radial, qui traverse le guide fixe 13 au travers d'une lumière 27 dont la longueur mesurée axialement, est au moins égale à l'amplitude maximale de la course du coulisseau 8, c'est-à-dire 2e si e est l'excentricité de la came 9 par rapport à l'arbre de rotation 10a. En regard de ce doigt 26, le guide fixe porte une butée 28 réglable en position par rapport à la lumière, suivant la direction de coulissement. Cette butée 28 est ici réalisée sous la forme d'un disque excentré par rapport à un axe de pivotement 29 et indexable angulairement autour de cet axe par des moyens non décrits et connus en eux-mêmes, qui peuvent comporter un bouton de réglage manuel. Ainsi, selon cette indexation, la butée 28 recouvre plus ou moins la lumière 27 et limite plus ou moins l'amplitude du mouvement du doigt 26 dans cette lumière.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 . Opposite this finger 26, 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. Thus, according to this indexing, 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.

Cette butée réglable constitue l'organe de réglage du débit de la pompe, toutes choses étant égales par ailleurs.This adjustable stop constitutes the pump flow adjustment member, all other things being equal.

On supposera tout d'abord que la butée 28 est dans une position découvrant une longueur de lumière 27 suffisante pour que le doigt 26 en puisse parcourir une longueur 2e. La rotation de la came excentrée 9 engendre un mouvement alternatif du coulisseau 8. Sa course vers l'avant (la gauche de la figure 1) constitue la phase de refoulement de la pompe. Sa course vers l'arrière (la droite de la figure 1) est la phase d'aspiration de la pompe. Pendant le refoulement, l'effort moteur développé par l'excentrique est transmis à la membrane par le coulisseau 8 les deux pièces 16 et 15 étant en appui l'une sur l'autre par leurs surfaces 18a, 17a. Pendant l'aspiration, l'effort moteur est transmis à la membrane au travers du mécanisme d'attelage 19, c'est-à-dire par le verrou de la pièce 15 sur la pièce 16 au moyen des billes.It will first be assumed that 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. During the discharge, 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. During suction, 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.

L'effort d'aspiration correspond à la colonne d'aspiration que l'on souhaite pouvoir élever avec la pompe et celui-ci peut aisément être supporté par le dispositif d'attelage 19 (choix approprié du ressort 23 et de son tarage pour des dimensions de billes déterminées). Pour un réglage de la pompe à sa capacité maximale de débit, l'équipage mobile se comporte donc comme un embiellage rigide.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). For an adjustment of the pump to its maximum flow capacity, the moving assembly therefore behaves like a rigid connecting rod assembly.

Pour obtenir une fraction du débit maximal on agit sur le disque 28 qui, débordant sur la lumière 27, va entraver la course du doigt 26. Lorsque ce dernier vient au contact du disque 28, la pièce 15 est bloquée dans sa course et l'effort résistant qu'elle subit surmonte l'effort de verrouillage. Les billes 20 et 21 s'effacent alors dans l'évidement 22 et la pièce 16 débrayée de la pièce 15 est seule entraînée par l'excentrique. Cet état est représenté à la figure 2. La quantité de produit aspirée dans la chambre 3 est donc limitée à une fraction de la quantité totale que cette chambre peut admettre du fait de l'arrêt prématuré du débattement vers l'arrière de la membrane 2.To obtain a fraction of the maximum flow rate, action is taken on the disc 28 which, overflowing into the lumen 27, will hinder the travel of the finger 26. When the latter comes into contact with the disc 28, the part 15 is blocked in its travel and the resistant effort that it undergoes overcomes the effort of locking. The balls 20 and 21 then disappear in the recess 22 and the part 16 disengaged from the part 15 is only driven by the eccentric. This state is shown in Figure 2. The amount of product sucked into the chamber 3 is therefore limited to a fraction of the total amount that this chamber can accept due to the premature cessation of the backward movement of the membrane 2 .

La figure 3 illustre le retour de la pièce 16 en direction de la pièce 15 qu'elle accoste par sa surface 18a sur la surface 17a de l'épaulement, puisqu'elle pousse en direction du point mort avant de la pompe pour refouler la quantité de produit précédemment aspirée. Dans le même temps, la gorge 24 permet aux billes 20 et 21 de retrouver leur place initiale et les deux pièces 15 et 16 sont à nouveau attelées.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. At the same time, 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.

Le cycle aspiration-refoulement se répète ainsi à chaque tour de l'excentrique. On notera que dès que les deux pièces sont débrayées, l'effort de retenue de la pièce 15 par la butée 28 est pratiquement nul. De même le couple résistant opposé à la rotation de l'excentrique pendant que les pièces 15 et 16 sont débrayées est également quasi nul. Il s'ensuit une dépense d'énergie et une usure des pièces en mouvement moindre. En outre, comme l'effort d'attelage est constant, le pouvoir d'aspiration de la pompe qui en dépend directement reste constant quel que soit le réglage de débit opéré. Le rendement global de la pompe est donc amélioré et reste bon quel que soit le régime de débit adopté.The suction-discharge cycle is thus repeated at each turn of the eccentric. It will be noted that as soon as the two parts are disengaged, the force for retaining the part 15 by the stop 28 is practically zero. Similarly, the resistive torque opposite the rotation of the eccentric while the parts 15 and 16 are disengaged is also almost zero. This results in an expenditure of energy and less wear on the moving parts. In addition, as the coupling force is constant, the suction power of the pump which directly depends on it remains constant regardless of the flow rate setting operated. The overall performance of the pump is therefore improved and remains good whatever the flow rate adopted.

Les figures 4A et 4B sont des vues en coupe d'une première réalisation pratique de l'invention, dans l'état de l'équipage mobile respectivement des figures 1 et 2. On retrouve sur ces figures certains des éléments déjà décrits avec les mêmes références. La pièce 15 est ici tubulaire avec un épaulement interne 30, pour recevoir une tige 31 comportant une extrémité 32 à la manière d'une soupape qui forme une surface de came coopérant avec les billes 20 et 21. Un ressort 33 est interposé entre l'épaulement 30 et un écrou 34 solidaire de la tige 31. Son effet tend à appliquer la partie 32 contre les billes 20 et 21 pour les extraire radialement de leur logement 22. L'écrou 34 permet d'ajuster le tarage du ressort 33, donc l'effort d'attelage des pièces 15 et 16 et en conséquence, le pouvoir d'aspiration de la pompe. On notera à cet égard que cet attelage débrayable constitue une sécurité de protection du mécanisme de la pompe. En effet si la canalisation 4 d'aspiration vient à se boucher, l'effort résistant peut augmenter jusqu'à surmonter l'effort d'attelage qui cèdera. On aura ainsi évité de soumettre la membrane à une contrainte trop importante qui pourrait conduire à sa rupture prématurée. Certaines membranes de forme sont en effet plus résistantes à l'égard de l'effort de refoulement qu'à l'égard de l'effort d'aspiration.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. It will be noted in this regard that this disengageable coupling constitutes a protection security for the pump mechanism. In fact, if the suction pipe 4 becomes blocked, 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.

A la figure 4C on retrouve les éléments décrits aux figures 4A et 4B avec les mêmes références. Le ressort 33 est ici interposé entre la pièce 16 et l'extrémité 32 de la tige 31 coulissante dans la pièce 16. L'intérêt de ce montage inversé réside dans la diminution de l'effort transmis par le ressort aux billes lorsque celles-ci sont escamotées dans leur logement, car l'attelage ayant été débrayé le ressort se détend lors de la poursuite de la course de la pièce 16.In Figure 4C we find the elements described in Figures 4A and 4B with the same references. The spring 33 is here interposed between the part 16 and the end 32 of the rod 31 sliding in the part 16. The advantage of this inverted assembly lies in the reduction of the force transmitted by the spring to the balls when the latter are retracted into their housing, because the hitch having been disengaged the spring relaxes during the continuation of the travel of the part 16.

Les figures 5A et 5B représentent chacune une variante des figures précédentes dans les mêmes états de l'équipage mobile. Dans ces réalisations également, la pièce 15 est tubulaire, l'alésage étant borgne du côté des billes 20 et 21. On mentionnera que les billes peuvent être d'un nombre supérieur à 2 et de préférence au nombre de trois, logées dans des perçages radiaux de la pièce 15 décalés de 120° les uns des autres. L'alésage 35 de la pièce 15 reçoit un poussoir coulissant qui peut affecter soit la forme d'un pointeau 36, soit celle d'une bille 37 (chacun de ces éléments étant à demi représenté sur les figures). Un ressort 38 est comprimé derrière ce pointeau 36 ou cette bille 37, pour les appliquer contre les billes 20, 21 afin de les forcer vers l'extérieur de la pièce 15. Un bouchon fileté 39 dans l'alésage 35 sert à régler le tarage du ressort 38. Une autre forme de réalisation de cette variante est illustrée par la figure 10 où le ressort 38 est constitué par un bloc d'élastomère 40 comprimé derrière la bille 37 par le bouchon fileté 39.FIGS. 5A and 5B each represent a variant of the preceding figures in the same states of the moving assembly. Also in these embodiments, the part 15 is tubular, the bore being blind on the side of the balls 20 and 21. It will be mentioned that 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. 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.

Aux figures 6A et 6B on a représenté, en dehors de certains éléments déjà décrits avec les mêmes références, une disposition inverse des précédentes en ce qui concerne la place des billes. Celles-ci 41 sont placées dans les logements 42 de la pièce 16 et sont contraintes de saillir vers l'intérieur de l'alésage 18 par des lamelles élastiques extérieures 43 logées dans une gorge 44 extérieure de la pièce 16 de façon à pouvoir se déformer sans être entravées par le guide 13. La partie 17 de la pièce 15 possède quant à elle une gorge 45 pour accueillir partiellement les billes 41 et prendre appui sur celles-ci par son flanc 46 tourné vers l'épaulement 17 a. La ou les lamelles élastiquement déformables 43 engendrent l'effort d'attelage des deux pièces 15 et 16 pour les mêmes raisons que celles données précédemment. La figure 6B est une image de la déformation élastique de ces lamelles lorsque les billes 41 sont forcées dans leur logement 42 après le débrayage de la liaison des pièces 15 et 16.In FIGS. 6A and 6B, apart from certain elements already described with the same references, there is shown a reverse arrangement of the preceding ones with regard to 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.

Le dispositif d'attelage représenté aux figures 7A et 7B est une sorte de pince élastique possédant une pluralité de dents élastiquement déformables 47 (réalisée par exemple par refendage d'un manchon cylindrique) solidaires de la pièce 15. Les extrémités 47a de ces dents sont engagées dans la gorge 24 de la pièce 16 dont l'un des flancs 25 forme surface de came pour soulever l'extrémité 47a de ces dents au moment du débrayage de la liaison. Les dents peuvent être remplacées par un manchon cylindrique avec un bourrelet extérieur susceptible de se rétreindre élastiquement.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.

Un autre mode de réalisation de l'invention est représenté aux figures 8A et 8B. La liaison débrayable des deux pièces est assurée ici par un cliquet 50 pivotant autour d'un axe 51 porté par la pièce 15. Cette dernière, contrairement aux réalisations précédentes, ne possède plus de partie coulissante dans l'alésage 18 de la pièce 16. La surface frontale 18a de cette pièce 16 prend appui sur l'extrémité 15a dressée de la pièce 15 et le cliquet 50 pivote dans une fente 52 de cette pièce 15. Lorsque les faces 18a et 15a sont en contact, l'extrémité 53 du cliquet peut s'engager dans la gorge 24 derrière son flanc 25 de la pièce 16. Cet engagement est forcé par un organe élastique 54 qui exerce son effort sur un levier 55 solidaire du cliquet et pivotant avec lui autour de l'axe 51. L'extrémité 56 de ce levier traverse le guide 13 par la lumière 27 pour coopérer avec la butée, le levier 55 bascule autour de l'axe 51 et soulève l'extrémité 53 qui sort de la gorge 24 et libère la liaison des pièces 15 et 16.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 latter, unlike the previous embodiments, no longer has a sliding part in the bore 18 of the part 16. 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. When the surfaces 18 a and 15 a are in contact, 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.

Lorsque la liaison est débrayée, l'effort du ressort 54 sur l'ensemble levier et cliquet est contré par les deux appuis de l'extrémité 53 sur la surface de l'alésage 18 et de l'extrémité 56 sur la butée 28. On notera enfin que la liaison des deux pièces est rétablie lorsque, d'une part les faces 15a et 18a sont en contact et, d'autre part, lorsque la pièce 15 a déjà été déplacée pour que le levier puisse à nouveau basculer sous l'effet du ressort 54.When the link is disengaged, the force of the spring 54 on the lever and pawl assembly is countered by the two supports of the end 53 on the surface of the bore 18 and of the end 56 on the stop 28. Note finally that the connection of the two parts is restored when, on the one hand the faces 15 a and 18 a are in contact and, on the other hand, when the piece 15 has already been moved so that the lever can switch on again the effect of spring 54.

Aux figures 9A et 9B enfin, on a représenté un dernier mode de réalisation de l'invention. La partie 17 de la pièce 15 est de diamètre inférieur à celui de l'alésage 18 de la pièce 16. L'espace annulaire ainsi existant permet de loger un ressort 57 comprimé entre un épaulement 58 porté par l'extrémité de la partie 17 et un épaulement 59 prévu à l'entrée de l'alésage 18. L'effort développé par le ressort plaque les surfaces 17a et 18a l'une contre l'autre et constitue l'effort d'attelage. Lorsque cet effort est surmonté, les pièces 15 et 16 peuvent se déplacer l'une par rapport à l'autre (figure 9B). Cette solution n'est applicable que pour des pompes à faible hauteur d'aspiration afin que l'effort d'attelage reste faible. En effet, contrairement aux autres réalisations, dans ce cas, pour un effort d'attelage donné, plus le débit est réglé à une faible valeur, plus le ressort est sollicité au delà de sa valeur de tarage et l'effort résistant croît au fur et à mesure que le ressort est comprimé lors du mouvement relatif des deux pièces, cet effort résistant étant transmis à la butée 28 par l'intermédiaire du doigt 26 de la pièce 15. C'est pourquoi il est préférable d'employer cette solution pour les pompes à faible valeur de tarage du ressort et à relativement faible variation des réglages du débit.Finally, in 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. the force generated by the spring plate surfaces 17a and 18a against each other and constitutes the coupling effort. When this effort is overcome, 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. In fact, unlike the other embodiments, in this case, for a given coupling force, the more the flow rate is set to a low value, the more the spring is stressed beyond its setting value and the resistance force increases as and as the spring is compressed during the relative movement of the two parts, this resistant force being transmitted to the stop 28 via the finger 26 of the part 15. This is why it is preferable to use this solution for pumps with a low spring setting value and a relatively small variation in flow settings.

Claims (15)

Equipage mobile d'entraînement alternatif de la membrane (2) d'une pompe à membrane actionnée mécaniquement, à course réglable, comprenant un coulisseau (8) monté glissant dans un guide (13) fixe, coopérant par l'une de ses extrémités avec un dispositif moteur (9-10) à excentrique, dont l'excentricité (e) définit l'amplitude (2e) maximale de la course du coulisseau (8) dans le guide (13) et attelé par son autre extrémité à la membrane (2), caractérisé en ce que le coulisseau (8) est télescopique avec deux pièces (15, 16) coulissantes, l'une par rapport à l'autre, parallèlement au guide (13), l'une motrice (16) étant attelée à l'excentrique (9), et l'autre (15) entraînée étant attelée à la membrane (2), les deux pièces étant, dans l'état rétracté du coulisseau (8), maintenues en appui l'une contre l'autre au moyen d'un organe (19) d'attelage développant un effort de maintien déterminé tandis que la pièce entraînée (15) du coulisseau (8) possède un organe de butée (26) coopérant avec une butée (28) réglable le long du guide (13), entravant la course de cette pièce (15) entraînée pour en limiter l'amplitude à une fraction de l'amplitude maximale (2e) engendrée par la rotation de l'excentrique (9) et opposant à l'effort de maintien un effort au moins égal, conduisant à l'extension du coulisseau (8).Movable alternating drive unit for the diaphragm (2) of a mechanically actuated diaphragm pump, with adjustable stroke, comprising a slide (8) mounted to slide in a fixed guide (13), cooperating at one of its ends with an eccentric motor device (9-10), whose eccentricity ( e ) defines the maximum amplitude (2 e ) of the stroke of the slide (8) in the guide (13) and coupled by its other end to the membrane (2), characterized in that the slide (8) is telescopic with two sliding parts (15, 16), one with respect to the other, parallel to the guide (13), the driving one (16) being coupled to the eccentric (9), and the other (15) driven being coupled to the membrane (2), the two parts being, in the retracted state of the slide (8), held in abutment one against the 'other by means of a coupling member (19) developing a determined holding force while the driven part (15) of the slide (8) poss edes a stop member (26) cooperating with a stop (28) adjustable along the guide (13), hampering the travel of this part (15) driven to limit the amplitude to a fraction of the maximum amplitude (2 e ) generated by the rotation of the eccentric (9) and opposing the holding force an at least equal force, leading to the extension of the slide (8). Equipage mobile selon la revendication 1, caractérisé en ce que l'organe d'attelage (19) comporte au moins un élément (20,21) mobile de verrouillage des deux pièces (15, 16) qui coopère avec une surface de came (25) portée par l'une des pièces (16) tendant à effacer radialement l'élément mobile (20, 21) dans un logement (22) prévu dans l'autre pièce (15), à l'encontre d'un organe élastique de rappel (23).Movable assembly according to claim 1, characterized in that the coupling member (19) comprises at least one movable element (20,21) for locking the two parts (15, 16) which cooperates with a cam surface (25 ) carried by one of the parts (16) tending to radially erase the movable element (20, 21) in a housing (22) provided in the other part (15), against an elastic member of reminder (23). Equipage mobile selon la revendication 1 ou la revendication 2 caractérisé en ce que l'extrémité de la pièce motrice (16) du coulisseau (8) opposée à l'excentrique (9) comporte un alésage (18) dans lequel est montée coulissante l'extrémité (17) de la pièce (15) entraînée opposée à la membrane (2), l'élément mobile de verrouillage étant constitué par une bille (20, 21) logée dans un évidement (22) ménagé radialement dans l'une des pièces soumise à l'effet d'un organe élastique (23) tendant à l'extraire de l'évidement, la surface de came étant constituée par le flanc (25) d'une gorge (24) ménagée dans l'autre pièce (16).Movable assembly according to claim 1 or claim 2 characterized in that the end of the driving part (16) of the slide (8) opposite the eccentric (9) has a bore (18) in which is mounted sliding the end (17) of the driven part (15) opposite the membrane (2), the movable locking element being constituted by a ball (20, 21) housed in a recess (22) formed radially in the one of the parts subjected to the effect of an elastic member (23) tending to extract it from the recess, the cam surface being constituted by the side (25) of a groove (24) formed in the other piece (16). Equipage mobile selon la revendication 3 caractérisé en ce que l'évidement (22) est prévu dans la pièce entraînée (15) et la gorge (24) dans la pièce motrice (16).Movable assembly according to claim 3 characterized in that the recess (22) is provided in the driven part (15) and the groove (24) in the driving part (16). Equipage mobile selon la revendication 4 caractérisé en ce que l'élément élastique (23) est disposé dans l'évidement radial (22).Movable assembly according to claim 4 characterized in that the elastic element (23) is disposed in the radial recess (22). Equipage mobile selon la revendication 4 caractérisé en ce que l'élément élastique (33,38) est constitué par un ressort logé axialement dans la pièce entraînée (15), interposé entre un appui (30,39) fixe de celle-ci et une came (32,36,37), coulissant axialement dans la pièce entraînée (15), qui s'appuie sous l'effet du ressort sur la bille (20,21) par une surface de came divergente.Movable assembly according to claim 4 characterized in that the elastic element (33,38) consists of a spring housed axially in the driven part (15), interposed between a fixed support (30,39) thereof and a cam (32,36,37), sliding axially in the driven part (15), which bears under the effect of the spring on the ball (20,21) by a diverging cam surface. Equipage mobile selon la revendication 6 caractérisé en ce que la came (31) ou la pièce entraînée (15) comporte un organe de réglage (34,39) du tarage du ressort (33,38).Movable equipment according to claim 6 characterized in that the cam (31) or the driven part (15) comprises a member (34,39) for adjusting the spring setting (33,38). Equipage mobile selon la revendication 6 ou la revendication 7, caractérisé en ce qu'il comprend une pluralité de billes (20,21) de verrouillage régulièrement réparties dans un même plan radial de la pièce entraînée (15).Movable assembly according to claim 6 or claim 7, characterized in that it comprises a plurality of locking balls (20,21) regularly distributed in the same radial plane of the driven part (15). Equipage mobile selon la revendication 3 caractérisé en ce que l'évidement (42) est prévu dans la pièce motrice (16) et la gorge (45), dans la pièce entraînée.Movable assembly according to claim 3 characterized in that the recess (42) is provided in the driving part (16) and the groove (45), in the driven part. Equipage mobile selon la revendication 9 caractérisé en ce que l'organe élastique est au moins une lamelle élastique (43) disposée dans une gorge (44) extérieure de la pièce (16) motrice dans laquelle débouche l'évidement.Movable assembly according to claim 9 characterized in that the elastic member is at least one elastic strip (43) disposed in a groove (44) outside of the driving part (16) into which the recess opens. Equipage mobile selon la revendication 2 caractérisé en ce que l'organe d'attelage comporte une griffe (47) solidaire de l'une des pièces (15), possédant une pluralité de dents (47) élastiquement déformables dans une direction radiale et dont les extrémités libres, formant élément mobile de verrouillage, sont engagées dans une gorge (24) de l'autre pièce (16), à l'état rétracté du coulisseau (8).Movable assembly according to claim 2 characterized in that the coupling member comprises a claw (47) integral with one of the parts (15), having a plurality of teeth (47) elastically deformable in a radial direction and whose free ends, forming movable locking element, are engaged in a groove (24) of the other part (16), in the retracted state of the slide (8). Equipage mobile selon la revendication 1 caractérisé en ce que l'organe d'attelage comporte un cliquet (50) de verrouillage pivotant sur la pièce entraînée (15) et engagé derrière une butée (25) de la pièce motrice lorsque le coulisseau est rétracté, sous l'effet d'un organe élastique (54), ce cliquet étant solidaire d'un levier (55) de manoeuvre dont l'extrémité libre (56) constitue l'organe de butée (26) de la pièce entraînée (15) pivotant à l'encontre de l'effet de l'organe élastique (54) dans le sens du dégagement du cliquet, lors de son contact avec la butée (28) réglable le long du guide.Movable assembly according to claim 1 characterized in that the coupling member comprises a pawl (50) pivoting on the driven part (15) and engaged behind a stop (25) of the driving part when the slide is retracted, under the effect of an elastic member (54), this pawl being integral with a lever (55) for operation, the free end (56) of which constitutes the stop member (26) of the driven part (15) pivoting against the effect of the elastic member (54) in the direction of release of the pawl, when it comes into contact with the stop (28) adjustable along the guide. Equipage mobile selon la revendication 1, caractérisé en ce que l'organe d'attelage est constitué par un organe élastique taré (57) disposé entre les deux pièces (15,16) du coulisseau et dont l'effet tend à maintenir le coulisseau dans sa position rétractée sous un effort déterminé.Movable assembly according to claim 1, characterized in that the coupling member is constituted by a calibrated elastic member (57) disposed between the two parts (15,16) of the slide and whose effect tends to keep the slide in its position retracted under a determined effort. Equipage mobile selon l'une quelconque des revendications précédentes, caractérisé en ce que l'organe élastique est constitué par une pièce en élastomère (40).Movable assembly according to any one of the preceding claims, characterized in that the elastic member consists of an elastomer part (40). Equipage mobile selon l'une quelconque des revendications 1 à 11 et 13, caractérisé en ce que la butée solidaire de la pièce entraînée (15) est un doigt (26) radial logé dans une lumière (27) longitudinale du guide fixe (13), la butée réglable (28) le long du guide étant constituée par un disque (28) excentré indexable angulairement autour d'un axe de pivotement (29) solidaire du guide (13) et parallèle au doigt (26) et recouvrant la lumière (27) sur une longueur dépendant de son indexation angulaire.Movable assembly according to any one of claims 1 to 11 and 13, characterized in that the stop integral with the driven part (15) is a finger (26) radial housed in a slot (27) longitudinal of the fixed guide (13) , the adjustable stop (28) along the guide being constituted by an eccentrically indexed disc (28) angularly around a pivot axis (29) integral with the guide (13) and parallel to the finger (26) and covering the light ( 27) over a length depending on its angular indexing.
EP91400633A 1990-03-29 1991-03-07 Telescopic mobile equipment for driving a reciprocating pump Expired - Lifetime EP0449686B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91400633T ATE97199T1 (en) 1990-03-29 1991-03-07 TELESCOPIC MOBILE EQUIPMENT TO DRIVE A DISPLACEMENT PUMP.

Applications Claiming Priority (2)

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FR9004020 1990-03-29
FR9004020A FR2660374B1 (en) 1990-03-29 1990-03-29 TELESCOPIC MOBILE EQUIPMENT FOR DRIVING AN ALTERNATIVE PUMP.

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EP0449686A1 true EP0449686A1 (en) 1991-10-02
EP0449686B1 EP0449686B1 (en) 1993-11-10

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EP (1) EP0449686B1 (en)
JP (1) JPH0758067B2 (en)
AT (1) ATE97199T1 (en)
CA (1) CA2038805A1 (en)
DE (1) DE69100609T2 (en)
ES (1) ES2047384T3 (en)
FR (1) FR2660374B1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0538123A1 (en) * 1991-10-17 1993-04-21 Pcm Pompes Diaphragmpump with continuously adjustable delivery between zero and a maximum value

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3373558B2 (en) * 1992-04-23 2003-02-04 松下電工株式会社 Small pump device
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 (en) * 2010-10-22 2012-11-16 Milton Roy Europe MEMBRANE PUMP WITH HIGH ASPIRATION CAPACITY
CN102937089B (en) * 2012-11-19 2016-01-20 浙江爱力浦泵业有限公司 A kind of mechanically actuated diaphragm metering pump transmission mechanism of diaphragm
US9709050B2 (en) * 2014-01-07 2017-07-18 Rocky Research Solution pump system
WO2019105969A1 (en) * 2017-11-28 2019-06-06 Koninklijke Philips N.V. Oral cleaning device with variable fluid pressurization
CN110454350A (en) * 2019-09-17 2019-11-15 郑州三惠机械设备有限公司 A kind of two-stage flux mill base feeding mechanism of colour mixer

Citations (4)

* 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
GB987441A (en) * 1960-10-21 1965-03-31 Wallace & Tiernan Inc Improvements relating to diaphragm pumps and drive mechanisms therefor
US4167896A (en) * 1977-08-11 1979-09-18 Gustafson, Inc. Pump for auger treater
FR2568530A1 (en) * 1984-08-03 1986-02-07 Marchal Equip Auto Windscreen washer device, comprising a pump associated with at least one windscreen wiper

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE7413016L (en) * 1974-10-16 1976-04-20 Piab Ab PUMP WITH FORWARD AND REVERSE PUMP ORGAN

Patent Citations (4)

* 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
GB987441A (en) * 1960-10-21 1965-03-31 Wallace & Tiernan Inc Improvements relating to diaphragm pumps and drive mechanisms therefor
US4167896A (en) * 1977-08-11 1979-09-18 Gustafson, Inc. Pump for auger treater
FR2568530A1 (en) * 1984-08-03 1986-02-07 Marchal Equip Auto Windscreen washer device, comprising a pump associated with at least one windscreen wiper

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0538123A1 (en) * 1991-10-17 1993-04-21 Pcm Pompes Diaphragmpump with continuously adjustable delivery between zero and a maximum value
FR2682720A1 (en) * 1991-10-17 1993-04-23 Pcm Pompes CONTINUOUSLY ADJUSTABLE FLOW PUMP PROCESS BETWEEN A ZERO VALUE AND A MAXIMUM VALUE AND ADJUSTABLE FLOW PUMP USING THE SAME.

Also Published As

Publication number Publication date
ES2047384T3 (en) 1994-02-16
DE69100609D1 (en) 1993-12-16
JPH04224287A (en) 1992-08-13
FR2660374A1 (en) 1991-10-04
CA2038805A1 (en) 1991-09-30
US5074763A (en) 1991-12-24
FR2660374B1 (en) 1992-07-03
EP0449686B1 (en) 1993-11-10
DE69100609T2 (en) 1994-06-01
JPH0758067B2 (en) 1995-06-21
ATE97199T1 (en) 1993-11-15

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