EP0078516A1 - Dispositif de pompage pour l'alimentation simultanée d'un dispositif pulvérisateur en au moins deux liquides à atomiser en proportion à choisir - Google Patents

Dispositif de pompage pour l'alimentation simultanée d'un dispositif pulvérisateur en au moins deux liquides à atomiser en proportion à choisir Download PDF

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Publication number
EP0078516A1
EP0078516A1 EP82109991A EP82109991A EP0078516A1 EP 0078516 A1 EP0078516 A1 EP 0078516A1 EP 82109991 A EP82109991 A EP 82109991A EP 82109991 A EP82109991 A EP 82109991A EP 0078516 A1 EP0078516 A1 EP 0078516A1
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EP
European Patent Office
Prior art keywords
pressure
valve
pump
piston
valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP82109991A
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German (de)
English (en)
Inventor
Edgar Müller
Markus Schmidhauser
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.)
J Wagner AG
Original Assignee
J Wagner AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by J Wagner AG filed Critical J Wagner AG
Publication of EP0078516A1 publication Critical patent/EP0078516A1/fr
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • F04B13/02—Pumps specially modified to deliver fixed or variable measured quantities of two or more fluids at the same time

Definitions

  • the invention relates to a pump device for the simultaneous supply of at least two atomizing liquids in a selectable ratio to a spraying device, consisting of a pneumatically or hydraulically actuated drive cylinder and driven by an adjustable balance beam, each of which pumps on the suction side with a supply for one of the atomizing liquid components and on the pressure side with the Sprayer is connected.
  • Such devices are generally designed so that a pneumatically operated, self-oscillating drive cylinder, which has either a mechanical-pneumatic or a fully pneumatic reversing device, drives a balance beam according to its movement.
  • the balance beam is mounted in an adjustable zero point, the zero point being adjusted by a threaded spindle or the like.
  • the feed pump for one of the two atomizing liquid components is arranged on one side of the zero point, usually in an axis extension to the driving drive cylinder, while the second pump is attached either at a distance to the same balance arm or to the end of the other balance arm.
  • the quantity ratio of the two components to one another is determined in the first case by changing the distance between the fastening points of the two pumps, in the second case by adjusting the zero point of the balance beam.
  • a disadvantage of these known pump devices is that when one of the two pumps is idling, for example because the container of one component has been sucked empty or because the suction of the pump on the suction side is disturbed or interrupted, for example by leaks in the suction system, the other, undisturbed pump continues to work unhindered, with the result that the operator usually does not recognize that only one of the two components is fed to the spraying device.
  • the object of the present invention is therefore to improve the pumping devices of the type mentioned at the outset in such a way that a fault in one of the two spray liquid pumps influences the overall operation of the pumping device in such a way that the fault is immediately recognizable or leads to an automatic shutdown.
  • the solution to this problem is characterized in the main claim.
  • the pressure drop occurring at the outlet of this pump in the event of a pump malfunction or the resulting pressure increase at the outlet of the other pump is used to actuate a bypass valve which then opens a bypass to the suction side of the assigned pump, with the result that the spray pressure changes clearly visible to the operator or the device is automatically switched off using the pressure change as a switching signal.
  • the bypass valves are designed as pressure relief valves.
  • the pressure increase in the other pump when the one pump is idling is used to actuate the pressure relief valve assigned to the undisturbed pump, which then opens a bypass to the suction side of this pump, with the result that neither of the two pumps works undisturbed, the spray pressure drops clearly visible or swan kung is subjected.
  • the bypass valves are designed such that they open the bypass when the liquid pressure falls below a predetermined minimum pressure.
  • one of the pumps malfunctions, such as a partial idle
  • the bypass to the suction side of the disturbed pump is opened, with the result that it runs completely empty, which is generally noticed by the person operating the spraying device.
  • this development of the invention is intended for an automatic shutdown of the device, in which case, by opening the bypass valve of the disturbed pump, a tappet valve mechanically coupled with it and seated in a pressure medium control line is closed, the interruption of the pressure medium Control line leads to a shutdown of the device.
  • the bypass valve of the other pump reacts in the case of the first development of the invention in the event of a fault in one pump
  • the bypass valve of the faulty pump itself reacts in the aforementioned development.
  • each pump can be assigned its own drive cylinder, the two drive cylinders being connected to one another in push-pull. This ensures that, in the case of idling of one of the two pumps, the pressure of the other pump rises significantly higher than when only a single drive cylinder is used, which considerably simplifies the setting and design of the pressure relief valves.
  • this assignment of a drive cylinder for each pump also improves the normal operation of the pump device, because it increases the pressure transmission ratio between the drive cylinder the and pump remains essentially the same even when the balance beam zero point is adjusted, i.e. when the component mixing ratio changes, between the drive cylinder and the pump.
  • the specified pressure transmission ratio between the drive cylinder and the pump is more favorable when using two drive cylinders.
  • compressed air is supplied at 10, the pressure of which is reduced by the reducing valve 11. 12 with a manometer and 13 with a pressure medium main valve.
  • the compressed air line then opens into a self-oscillating drive cylinder 14, which represents a compressed air motor has a mechanical-pneumatic or a fully pneumatic reversing device 14c (not shown).
  • the piston of the drive cylinder 14 is 14a, the piston rod 14b.
  • Compressed air lines 15 and 16 extend from the two cylinder spaces of the drive cylinder 14 and lead to the two cylinder spaces of a second drive cylinder 17, the piston of which is designated 17a and the piston rod 17b.
  • a balance beam 18 is connected at point 19 to the piston rod 14b and at point 20 to the piston rod 17b, the center point of the balance beam 18 being designated 21; the center of the beam 21 is designed to be displaceable.
  • the piston rod 14b of the drive cylinder 14 drives a piston pump 22, the piston rod 17b of the drive cylinder 17 drives a piston pump 23.
  • the piston pump 22 draws paint from a first paint container 24, the piston pump 23 from a second paint container 25.
  • the paint outlet of the piston pump 22 leads via a manometer 26, a pressure relief valve 27 and a check valve 28 to a mixing tube 29.
  • a bypass is indicated at 30, which leads from the pressure relief valve 27 to the first paint container 24.
  • the paint outlet of the piston pump 23 leads to the mixing tube 29 via a pressure gauge 31, a pressure relief valve 32 and a check valve 34; a bypass 34 connects the pressure relief valve 32 to the second paint container 25.
  • a line 35 leads from the outlet of the mixing tube 29 to a paint spray gun (not shown).
  • the pressure relief valve 27 and the pressure relief valve 32 identical to it is shown in FIG. 2.
  • the pressure relief valve has a housing 40 with an ink opening 41 and an overflow opening 42, in which housing 40 a differential piston 43 is mounted, which is supported by a coil spring 44 against the ink opening 41 is loaded that he closes it in the normal position.
  • the pumping device works as follows.
  • the compressed air supplied via line 10 and reduced in pressure by valve 11 drives drive cylinder 14 in the desired manner.
  • the piston 14a of the cylinder 14 drives the piston of the paint pump 22 via the piston rod 14b, so that this paint sucks from the paint container 24, pressurizes it in the pump chamber and feeds it to the mixing tube 29 through the pump outlet line via the check valve 28.
  • the outlet lines 15, 16 leading away from the drive cylinder 14 are connected - crosswise - to the cylinder spaces of the second drive cylinder 17 located on both sides of the piston 17a, ie the piston 17a is caused to oscillate via the compressed air lines 15, 16. Is the zero point 21 - as shown in the drawing - exactly in the middle between its articulation points 19 and 20 on the piston rods 14b and 17b, then the two pistons 14a and 17a oscillate with the same stroke size and stroke speed in push-pull.
  • the second paint pump 23 is driven in the same way - albeit in push-pull - as the paint pump 22, ie the pump 23 draws in the same amount of paint from the container 25, sets the paint under the same pressure and conveys the paint through the pump outlet line the check valve 33 through to the mixing tube 29.
  • the spray device Via the line 35, the spray device is supplied with a paint mixture with a mixing ratio of 1: 1 of the two paint components.
  • this mixture ratio changes when the zero point 21 of the Balance beam 18 is moved, this zero-point adjustment is preferably carried out by a - not shown - threaded spindle.
  • the stroke of the piston 17a of the drive cylinder 17 is reduced compared to the stroke of the piston 14a of the drive cylinder 14, with the result that the delivery rate of the ink pump 23 decreases compared to the delivery rate of the ink pump 22 .
  • the paint mixture supplied via line 35 to the spraying device then has a different mixing ratio; in the case of the above-mentioned shift of the zero point 21 to the right, the proportion of the color component of the container 25 decreases compared to the color component of the container 24.
  • FIGS. 3 and 4 the flutter indicating the fault indicating the piston of the pressure relief valve and thus the spray pressure is damped, with the aim of automatically switching off the entire pump system when idling To be able to bring about the pump cylinder.
  • the pump system shown in Fig. 3 differs from that of Fig. 1 only in that from the compressed air supply line, namely after the safety shut-off valve 13, branch gen 50, 51 lead to the two, here designated 52 and 53 pressure relief valves.
  • the structure of the two identical pressure relief valves 52, 53 can be seen in FIG. 4.
  • the parts corresponding to the pressure relief valve of FIG. 2 are provided with the same reference numerals.
  • the compressed air inlet 54 connected to the line 50 or 51, an auxiliary piston 55, a throttle 56 and a damping chamber 57 filled with a hydraulic fluid.
  • the pressure of the piston 43 against the ink opening 41 is therefore not caused here by a spring, but by the supply pressure of the compressed air supply, under which the two drive cylinders 14, 17 are also located.
  • the compressed air displaces the auxiliary piston 55 to the right and thereby presses hydraulic fluid through the throttle 56 into the space 57, with the result that the hydraulic fluid presses the piston 43 to the left against the paint opening 41 and thereby closes the paint opening.
  • the structure of the pressure relief valves can be modified, for example in such a way that the valves 27, 32 also receive a compressed air connection, in such a way that the spring only provides an additional auxiliary force.
  • the return lines 30, 34 can also return directly to the suction lines of the pumps 22, 23, which shortens the return path.
  • FIGS. 5-7 Another embodiment of the invention is shown in FIGS. 5-7. 5, compressed air is supplied at 10, the pressure of which is reduced by the reducing valve 11. With 12 is a manometer and 13 denotes a safety shut-off valve. The compressed air line then opens into a self-oscillating drive cylinder 14 which represents a compressed air motor and which has a mechanical-pneumatic or a fully pneumatic reversing device 14c (not shown). The piston of the drive cylinder 14 is 14a, the piston rod is 14b. Compressed air lines 15 and 16 extend from the two cylinder spaces of the drive cylinder and lead to the two cylinder spaces of a second drive cylinder 17, the piston of which is designated 17a and the piston rod 17b. A balance beam 18 is connected at point 19 to the piston rod 14b and at point 20 to the piston rod 17b, the center point of the balance beam 18 being designated 21; the center of the beam 21 is designed to be displaceable.
  • the piston rod 14b of the drive cylinder 14 drives a piston pump 22, the piston rod 17b of the drive cylinder drives a piston pump 23.
  • the piston pump 22 draws paint from a first paint container 24, the piston pump 23 from a second paint container 25.
  • the paint outlet of the piston pump 22 leads via a pressure gauge 26, a pressure relief valve 27 and a check valve 28 to a mixing tube 29, 30 denotes a bypass which leads from the pressure relief valve 27 to the first paint container 24.
  • the paint outlet of the piston pump 23 leads to the mixing tube 29 via a pressure gauge 31, a pressure relief valve 32 and a check valve 33; a bypass 34 connects the pressure relief valve 32 to the second paint container 25.
  • a line 35 leads from the outlet of the mixing tube 29 to a paint spray gun (not shown).
  • valve chambers 62a and 62b are connected to the bypass 30 and the bypass 3Z4 via outlet bores 65a and 65b, the bores 65a and 65b being located within that wall area of the valve chamber 62a and 62b which can be passed over by the piston 61.
  • the pumping device works as follows.
  • the compressed air supplied via line 10 and reduced in pressure by valve 11 drives drive cylinder 14 in the desired manner.
  • the piston 14a of the cylinder 14 drives the piston of the paint pump 22 via the piston rod 14b, so that this paint sucks from the paint container 24, pressurizes it in the pump chamber and through the pump outlet line via the valve chamber 62a and the check valve 28 to the mixing pipe 29 feeds.
  • the outlet lines 15, 16 leading away from the drive cylinder 14 are connected - crosswise - to the cylinder spaces of the second drive cylinder 17 located on both sides of the piston 17a, i.e. the piston 17a is caused to oscillate via the compressed air lines 15, 16.
  • the two pistons 14a and 17a oscillate with the same stroke size and stroke speed in push-pull.
  • the second ink pump 23 is driven in the same way - albeit in a push-pull manner - like the ink pump 22, i.e.
  • the pump 23 draws in the same amount of paint from the container 25, pressurizes the paint and then conveys the paint through the pump outlet line via the valve chamber 62b and the check valve 34 to the mixing tube 29.
  • the line 35 thus mixes the support device with the paint a mixing ratio of 1: 1 of the two color components.
  • this mixing ratio changes when the zero point 21 of the balance beam 18 is shifted, this zero point adjustment preferably being carried out by a threaded spindle (not shown). It is essential that the use of two drive cylinders 14, 17 with such a zero point adjustment of the balance beam 18 results in the desired change in the ink delivery quantities, but the ink pressures remain essentially the same because there is no change in the pressure transmission ratios between the two cylinders 14, 17 and the two pumps 22, 23 occurs.
  • FIG. 7 shows a modification of the pressure relief valves 27, 32 accommodated in a common housing 60.
  • This embodiment differs from that according to FIG. 6 only in that the piston 61 has a relief bore 68a and 68b on both sides.
  • These additional relief bores have the advantage that when the higher pressure side (after the failure of the other pump) moves the piston 61 into an end position, the valve chamber of the pressure-free sides is also connected to the associated return line, that is to say completely relieved of pressure.
  • this embodiment brings advantages if residual quantities are still being conveyed by the pump which is defective; in this case, the associated valve chamber is then immediately vented, despite the still low effect of the faulty pump, so that the failure is immediately noticeable.
  • the pressure relief valve of Fig. 8 operates as follows. If one of the two pumps 22, 23 runs idle in the device described at the outset, the pressure rises considerably on the high-pressure side of the pump which is still working properly. The result of this is that the pressure relief valve assigned to this pump, for example the pump 23, that is to say the pressure relief valve 32 for example, opens, ie the piston 43 is displaced to the right against the force of the spring 44. As soon as the forehead of the piston 43 has passed the bolt 70, this is pressed down by the force of the spring 71 in front of the piston end. In other words, the latch 70 lies in front of the piston and holds it in the open position of the valve.
  • FIG. 9 shows a further, particularly expedient embodiment of the invention.
  • the structure of the device essentially corresponds to the structure of the device according to FIG. 1, the same and similar components being provided with the same reference numerals.
  • the compressed air main valve 13 inserted into the compressed air supply line 10 has a different construction than that of the embodiment of FIG. 1.
  • the valve 13 according to FIG. 9 has, in addition to the main inlet of the line 10, a second compressed air inlet which is connected to one of a compressed air line 80a leading to a starter valve 80 is connected.
  • the main valve 13 has two switching positions, its outlet being connected to the main inlet (line 10) in one switching position and to the secondary inlet (line 80a) in the other switching position.
  • the valve is switched pneumatically, the control air being supplied through a control line 13a, which branches off from the main line 10 downstream of the control valve 13 and is returned to the main valve 13.
  • the mentioned starter valve 80 is connected in parallel to the main valve 13, ie its inlet is connected to the line 10 upstream from the main valve 13, and, as mentioned, its outlet leads via line 80a to the secondary inlet of the main valve 13.
  • the starter valve can be operated manually, that it is open in normal position (passage blocked), but can be closed (switched to passage) by manually pressing a button against spring pressure.
  • the bypass valves used in the pressure side of the pumps 22 and 23, designated 27 and 32 in FIG. 1, are designated 81 and 82 in FIG. 9 because they have a different structure.
  • Tappet valves 83 and 84 are mechanically coupled to the valves 81 and 82 and are connected in series in the control line 13a mentioned. The structure of the valves 81, 82, 83 and 84 results from FIG. 10.
  • the bypass valve 81 is identical to this, has a valve body 90 which is penetrated by a valve tappet 91 with a conical valve body 91a.
  • Designated at 92 is a liquid chamber which communicates with a liquid inlet and a liquid outlet (not shown in the drawing) on diametrically opposite sides, so that the liquid line leading from the pressure outlet of the pump 22 to the inlet of the mixer 29 is passed through this chamber 92 .
  • the chamber 92 is covered by a membrane 93.
  • An air piston 94 is located on the valve tappet 91 and seals an air chamber 95 into a partial chamber 95a and a partial chamber 95b.
  • the sub-chamber 95a is connected to a branch air line 80b, which extends from the outlet line 80a of the starter valve 80, while the sub-chamber 95b is connected to a compressed air branch line 13b, which extends from the main line 10 between the main valve 13 and the drive cylinder 14.
  • a bypass transverse bore 96 is provided in the valve housing 90, to which the return line 24 is connected.
  • the housing 97 of the above-mentioned tappet valve 83 is attached to the housing 90 of the bypass valve 81, a valve tappet 98 abutting against the diaphragm 93, on the side opposite the valve body 91a.
  • the valve tappet 98 switches the tappet valve 83 into the open or closed position when it is displaced in a manner which is not shown but is customary.
  • valve body 91a sits on its valve seat, so that the bypass 96 is not in communication with the liquid chamber 92.
  • the tappet valve 83 is open, ie the air passage is blocked.
  • the device according to FIGS. 9 and 10 operates as follows. To start, the starter valve is pressed and held in the pressed position. Thus compressed air from line 1ß passes through starter valve 80 and from there, on the one hand, via main valve 13 and line 10 to drive cylinder 14 and further to drive cylinder 17, whereby these two cylinders and thus also pumps 22 and 23 are in operation be set. At the same time, air flows via line 13b into the compressed air subchamber 95a of the two bypass valves 81 and 82, with the result that the cone valve body 91a is pressed firmly onto its seat, that is to say the two bypass lines are closed.
  • compressed air flows via line 80b into the air sub-chamber 95b, specifically via line 13b, with which a certain back pressure is achieved on the piston 94 in the direction of an open one of the bypass 96, but this back pressure, possibly due to a small area difference of the piston 94 is not sufficient to open the bypass.
  • pressurized liquid succeeded in the liquid chamber 92 of the bypass valves 81, 82, with the result that the diaphragms 94 bulge and thereby switch the plunger valves 83 and 84 to pass through the plunger 98 .
  • control air is supplied via line 13a to the control side of the main valve 13, so that the main valve 13 switches to passage and blocks the shunt via the starter valve 80.
  • the starter valve can now be released, whereby line 80b is also switched off.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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EP82109991A 1981-11-02 1982-10-28 Dispositif de pompage pour l'alimentation simultanée d'un dispositif pulvérisateur en au moins deux liquides à atomiser en proportion à choisir Ceased EP0078516A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3143405 1981-11-02
DE3143405 1981-11-02
DE3214313 1982-04-19
DE3214313 1982-04-19

Publications (1)

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EP0078516A1 true EP0078516A1 (fr) 1983-05-11

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EP82109991A Ceased EP0078516A1 (fr) 1981-11-02 1982-10-28 Dispositif de pompage pour l'alimentation simultanée d'un dispositif pulvérisateur en au moins deux liquides à atomiser en proportion à choisir

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2183739A (en) * 1985-12-05 1987-06-10 Takeshi Hoya Pumping plant
EP0311792A2 (fr) * 1987-10-15 1989-04-19 Wagner International Ag Dispositif de pompage pour l'alimentation simultanée de deux liquides à un dispositif atomiseur
EP0350605A2 (fr) * 1988-07-12 1990-01-17 Wagner International Ag Installation de pulvérisation d'un produit à 2 composants
DE3823606C1 (en) * 1988-07-12 1990-01-18 Wagner International Ag, Altstaetten, Ch Two-component spraying device
FR2731919A1 (fr) * 1995-03-23 1996-09-27 Mancel Patrick Dispositif d'alimentation d'un moyen de distribution en une composition a deux composants dont on peut faire varier les proportions respectives

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2049884A1 (de) * 1969-10-16 1971-04-29 Borg Warner Corp , Chicago, 111 (V St A) Hydrauliksystem
US4030860A (en) * 1976-03-15 1977-06-21 Standlick Ronald E Variable proportional metering apparatus
DE2646606A1 (de) * 1976-10-15 1978-04-20 Hans Werner Beil Verfahren zum dosieren von fluessigkunststoffen mittels kolbenpumpen durch hydraulische verkoppelung von hubzylindern
FR2396184A1 (fr) * 1977-06-29 1979-01-26 Allibe Ateliers & Co Machine pour le dosage volumetrique reglable de composants liquides
US4171191A (en) * 1976-03-25 1979-10-16 Krueger Wallace F Apparatus for transferring metered quantities of material from one location to another
FR2424070A1 (fr) * 1978-04-28 1979-11-23 Skm Sa Dispositif d'alimentation a debit constant de fluide, notamment pour pistolet de pulverisation
FR2451228A2 (fr) * 1979-03-16 1980-10-10 Skm Sa Dispositif d'alimentation a debit constant de fluide, notamment pour pistolet de pulverisation

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2049884A1 (de) * 1969-10-16 1971-04-29 Borg Warner Corp , Chicago, 111 (V St A) Hydrauliksystem
US4030860A (en) * 1976-03-15 1977-06-21 Standlick Ronald E Variable proportional metering apparatus
US4171191A (en) * 1976-03-25 1979-10-16 Krueger Wallace F Apparatus for transferring metered quantities of material from one location to another
DE2646606A1 (de) * 1976-10-15 1978-04-20 Hans Werner Beil Verfahren zum dosieren von fluessigkunststoffen mittels kolbenpumpen durch hydraulische verkoppelung von hubzylindern
FR2396184A1 (fr) * 1977-06-29 1979-01-26 Allibe Ateliers & Co Machine pour le dosage volumetrique reglable de composants liquides
FR2424070A1 (fr) * 1978-04-28 1979-11-23 Skm Sa Dispositif d'alimentation a debit constant de fluide, notamment pour pistolet de pulverisation
FR2451228A2 (fr) * 1979-03-16 1980-10-10 Skm Sa Dispositif d'alimentation a debit constant de fluide, notamment pour pistolet de pulverisation

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2183739A (en) * 1985-12-05 1987-06-10 Takeshi Hoya Pumping plant
EP0311792A2 (fr) * 1987-10-15 1989-04-19 Wagner International Ag Dispositif de pompage pour l'alimentation simultanée de deux liquides à un dispositif atomiseur
EP0311792A3 (en) * 1987-10-15 1990-04-25 Wagner International Ag Pumping arrangement for the simultaneous feeding of two liquids to a spray apparatus
EP0350605A2 (fr) * 1988-07-12 1990-01-17 Wagner International Ag Installation de pulvérisation d'un produit à 2 composants
DE3823606C1 (en) * 1988-07-12 1990-01-18 Wagner International Ag, Altstaetten, Ch Two-component spraying device
EP0350605A3 (fr) * 1988-07-12 1990-09-19 Wagner International Ag Installation de pulvérisation d'un produit à 2 composants
FR2731919A1 (fr) * 1995-03-23 1996-09-27 Mancel Patrick Dispositif d'alimentation d'un moyen de distribution en une composition a deux composants dont on peut faire varier les proportions respectives

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