EP0592395B1 - Pumpeinheit mit zwei verdrängerpumpen - Google Patents

Pumpeinheit mit zwei verdrängerpumpen Download PDF

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Publication number
EP0592395B1
EP0592395B1 EP90915533A EP90915533A EP0592395B1 EP 0592395 B1 EP0592395 B1 EP 0592395B1 EP 90915533 A EP90915533 A EP 90915533A EP 90915533 A EP90915533 A EP 90915533A EP 0592395 B1 EP0592395 B1 EP 0592395B1
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EP
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Prior art keywords
pump
hydraulic
conduit
driving
port
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EP90915533A
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English (en)
French (fr)
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EP0592395A1 (de
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Henrik Kitsnik
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Individual
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Individual
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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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders

Definitions

  • the present invention relates to pump assembly comprising a first and second pump unit, each comprising a pump housing chamber, a pump housing cylinder and a displacement element movably mounted in said pump housing cylinder, said displacement element, during a pump stroke being driven into said pump housing chamber; said first pump unit further comprising a first driving unit for the displacement element of said first pump unit, said first driving unit comprising a first hydraulic cylinder with a first driving piston in said hydraulic cylinder and a driving rod, connecting said first driving piston with said displacement element; said second pump unit further comprising a second driving unit for the displacement element of said second pump unit, said second driving unit comprising a second hydraulic cylinder with a second driving piston in said hydraulic cylinder and a driving rod connecting said second driving piston with said displacement element of said second pump unit; said pump assembly further comprising a source of hydraulic medium, and a first hydraulic pump for supplying said first and second pump units with hydraulic medium under pressure.
  • Displacement pumps are known and designed in many ways.
  • a piston is defined in this text as a piston provided with one or several sealing elements, which interact with a smooth cylinder wall
  • a plunger in this text is defined as a piston having a smooth, cylindrical outer surface, which interacts with one or several sealing elements, mounted in a cylindrical wall, which does not have to be smooth.
  • a piston is in this context a machine element, which can function as either a piston or a plunger.
  • DE-A-2010112 discloses two co-operating hydraulic displacement pumps and a regulation system which includes a plurality of values for controlling the flow of hydraulic medium and also two shut-off valves for the pumped medium, which do not allow any moderated flow of the pumped medium and hence no measures to avoid pulsations.
  • the object of the present invention is to achieve improvements in displacement pumps and particularly in plunger pumps.
  • the object of the invention is to solve the above-mentioned problems.
  • the plunger pump assembly comprises according to a first preferred embodiment two pump units or cylinders A,B, the shiftings of which are controlled by a common, particularly designed sliding valve V.
  • the equipment also includes a hydraulic assembly, which generally is designated H.
  • the two pump units A and B are identically designed and equipped. Thus, in the following text only one of the pump units, the A-unit, will be described in more detail. When it is required to understand the functional description, numerical references to elements belonging to the A-unit have been given the addition A, whereas the corresponding elements of the B-unit have obtained the addition B in the drawings and/or in the text.
  • the A-unit comprises a pump housing 1A and a driving unit 2A.
  • Pump housing 1A includes a pump housing chamber 5A having an inlet conduit with a nonreturn valve 3A and an outlet conduit with a nonreturn valve 4A.
  • a sealing housing 6A is connected to pump housing 1A and is an integrated part of pump housing 1A and forms a continuation of the cylinder-shaped pump housing chamber 5A, but its interior dimensions are smaller.
  • a rinsing water housing 7A and a draining housing 8A are connected to sealing housing 6A.
  • a housing or spacing piece between driving unit 2A and the pump housing and its sealing housing 6A is designated 9A.
  • a plunger is designated 10A.
  • Driving unit 2A comprises the following main elements: a hydraulic cylinder 11A, a driving piston 12A, a driving rod 13A, which connects driving piston 12A to plunger 10A, an end block 14A and a top lid 15A.
  • Elements 1A, 6A, 7A, 8A,9A,11A,14A,15A are connected to each other by means of bolted joints to one unit.
  • the unit, which comprises plunger 10A, driving piston 12A and driving rod 13A is movable between two end positions.
  • Plunger 10A has a smooth cylindrical exterior surface, which is designed to interact with a number of annular or sleeve-shaped sealings in sealing housing 6A, which also is a part of the pump housing cylinder.
  • a secondary sealing sleeve is designated 18 and a third sealing is designated 19. The latter seals against the ambient air, which fills the space 58 inside spacing piece 9A.
  • a lower guide between sealing sleeves 17 and 18 is designated 20 and an upper guide outside sealing 19 is designated 21.
  • sealing housing 6A Elements 17-21 are placed in annular grooves in sealing housing 6A. Also, the interior wall of sealing housing 6A has a profile in cross-section, in which there is an annular gap-shaped space 22 inside and above the combined main sealing, comprising wiper 17, an annular recess 23 inside and below secondary sealing 18 and an annular space 24 between secondary sealing 18 and third sealing 19, which is turned outwards.
  • conduit 26 leads to annular space 24 and from this space a conduit 25 leads, branching off into a conduit 26 up towards draining housing 8A and a conduit 27 downwards to a nonreturn valve 28, on the downstream-side of which there is a conduit 29, which via a connection conduit 30 leads to annular spaces 22 and 23.
  • An inlet conduit 32 for rinsing water is extended via a nonreturn valve 33 into a rinsing water chamber 34, which communicates with the above-mentioned conduit 26, which is extended into annular space 24 in sealing housing 6A.
  • a rinsing plunger 35 with a screw-wound spring 36 on its inside, which strives to push plunger 35 upwards against a hydraulic, small control plunger 37, mounted in a hydraulic control cylinder 38.
  • Draining housing 8A comprises a cylinder with a hydraulic piston 40 having a hydraulic rod 41, which exerts a pressure against a nonreturn valve ball 48, which in Fig. 1A blocks the passage between conduit 26 and adraining conduit 39.
  • a return spring for piston 40 is designated 49.
  • Hydraulic cylinder 11A in driving unit 2A is on one side of piston 12A provided with a driving or plus chamber 42A and on the other side with a return or minus chamber 43A.
  • Piston 12A has an axial cavity 50A, which also extends a small distance into driving rod 13A. Cavity 50A communicates via ducts 51A with an annular gap 52A in the middle of piston 12A. A duct, which extends throughhydraulic cylinder 11A of the driving unit a small distance from outer gap 45A of the return chamber, is designated 53A. In top lid 15A there is a central opening, into which a tube 54A is screwed, which has the same length as and extends into axial cavity 50A in driving piston 12A and driving rod 13A. A sealing between the outer side of tube 54A and the outer end of space 50A is designated 55.
  • a large aeration duct 57 connects space 58 inside housing 9A with the outside.
  • central valve V there is a slide 60, which is provided with a first, a second, a third and a fourth flange 61-64, designed to slide along the inside of the valve housing. Between said flanges there is a left annular recess 65, a central annular recess 66 and a right annular recess 67.
  • Hydraulic assembly H includes according to this embodiment a sump 70, a first hydraulic pump 71, which is the main pump in the system and an auxiliary pump 72.
  • the system comprises a number of hydraulic conduits. Those conduits, which mainly are connected to the A-unit, have obtained the addition A, and those which mainly belong to the B-unit have been given the designation B.
  • a main conduit 80 leads to control valve V, and the hydraulic oil, which flows through conduit 80, can via central recess 66 in slide 60 be distributed either to a driving conduit 82A to gap 44A or to a driving conduit 82B to a corresponding gap 44B in the B-unit, or via the two driving conduits 82A and 82B to the two units A and B, dependent on the position of slide 60.
  • the hydraulic oil in driving chambers 42A and 42B can also be emptied through conduits 82A and 82B via said right recess 67 and a draining conduit 83A as well as via said left recess 65 and a draining conduit 83B respectively.
  • Return chambers 43A and 43B can at the return stroke be filled with hydraulic oil by means of auxiliary pump 72 via a conduit 81 and a conduit 84A, which leads to gap 45A, and via conduit 81 and a conduit 84B which leads to gap 45B respectively.
  • the oil in return chambers 43A and 43B can be emptied in the same way.
  • the oil from conduit 81 flows to sump 70 via a conduit 85 past an overflow valve 96.
  • gaps 45A and 45B communicates directly with each other via conduits 84A and 84B, which belong to the common pressurized return system, in which a constant pressure is maintained by pump 72 and overflow valve 96.
  • a conduit 86A leads to control cylinder 38 in rinsing water housing 7A.
  • a conduit 87A leads to the cylinder in draining housing 8A.
  • a conduit 88A leads to central tube 54A.
  • a control conduit 89A and 89B respectively leads from duct 53A in end block 14A as well as from the corresponding duct in the B-unit respectively to the respective ends of control valve V respectively.
  • control conduits 89A and 89B there is a restriction 68A and 68B respectively.
  • Those pump units which have been described with reference to Figs. 1A-1C and Fig. 4 are particularly designed to be used when the pump medium has a moderate pressure, i.e. up to a maximum of 100 bar, e.g. 50-60 bar, but it is possible to use a considerably higher hydraulic pressure in order to, by reducing the pump medium pressure, instead increase the outlet flow of the pump as compared to the driving oil flow.
  • a moderate pressure i.e. up to a maximum of 100 bar, e.g. 50-60 bar
  • Return chamber 43B is fed with hydraulic oil from return chamber 43A of the A-unit, from which the hydraulic oil is pressed out via conduit 84A.
  • Auxiliary pump 72 contributes to maintaining the pressure in return system 43A-43B.
  • a certain amount of oil is recirculated through conduit 85.
  • the hydraulic oil in driving chamber 42B of the B-unit is drained through conduit 82B, gap 65 and draining conduit 83B.
  • the oil in cavity 50B and in tube 54A is drained through conduits 88B,83A. This phase is indicated by the continuously drawn horizontal curve of the A-unit and the dashed line-drawn inclined curve of the B-unit to the left of position I in Fig. 2A.
  • driving piston 12B In position I driving piston 12B reaches its upper end position and remains in this position up to position II, while driving piston 12A continues to move forwards an additional distance with the same speed up to position II.
  • Flange 62 closes the connection between conduit 82B and draining conduit 83B.
  • Flange 62 passes conduit 82B, and now hydraulic oil from main conduit 80 can be distributed to the two conduits 82A and 82B via central gap 66 in valve V.
  • the B-unit is pressurized through driving chamber 42B, which means that driving piston 12B starts its movement forwards (downwards, Fig. 1).
  • main pump 71 feeds a constant flow of hydraulic fluid through conduit 80, the feeding to driving chamber 42A will decrease with the same amount which is now fed into driving chamber 42B in the B-unit, which corresponds to the inclined portions and curves in Fig. 2A between positions II and III, and means that driving piston 12B is accelerating, while driving piston 12A is decelerating to the same extent.
  • the Y-ratio Y37:Y35 is to be larger than the ratio Y12A:Y10A to such an extent that the pressure Pv on the rinsing water in rinsing water housing 7A (also considering the force exerted by spring 36 and various other factors) is somewhat larger than pressure Pp on the pump medium in pump housing chamber 5A.
  • pressure Ph will be sufficiently large to be able to, via conduit 87A and piston 40, compress spring 44 in draining housing 8A and close nonreturn volve 42.
  • control plunger 37 is actuated by the pressure in control cylinder 38, it will press rinsing plunger 35 against spring 36.
  • Nonreturn valve 33 will be closed.
  • the obtained pressure in rinsing water chamber 34 is propagated through conduit 26 in sealing housing 6A into gap 24 and from the gap through ducts 25 and 27, past nonreturn valve 28 and through duct 29 into duct 22 inside and behind the combined primary sealing and wiper 17.
  • the pressure difference between the rinsing water pressure in gap 22 and the pump medium pressure in pump housing chamber 5A would be larger than the contact force for the wiper lip on primary sealing 17, the rinsing water would be pressed past the sealing into the pump chamber, until an equilibrium is obtained between the rinsing water pressure, the contact force on the sealing as well as the pump medium pressure.
  • rinsing plunger 35 will move downwards concurrently with the rinsing water flow past primary sealing 17.
  • the plunger sealings are to be arranged in such a way, that a considerably reduced wear on the plunger and on its sealings is attained, when liquids are pumped, which contain solid and/or wearing particles.
  • This is achieved mainly by using a wiper, which works in the way described above as a primary sealing against the pump medium. Since wipers having the configuration shown in the drawings normally are not able to perform at pressure differences corresponding to the working pressure of the pump, according to the invention a pressure equilibrium of the combined primary sealing/wiper 17 by means of the rinsing water pressure, which is active in gap 22, has been achieved, and thus mainly the same pressure is used on either side of the wiper during the pump stroke.
  • the rinsing water on the rear side of primary sealing/wiper 17 has a somewhat higher pressure than the pressure used in pump housing 5A, which prevents the pump medium from being pressedup into the spaces above the primary sealing, if the same possibly has been damaged.
  • secondary sealing 18 will obtain a pressure equilibrium, when rinsing water having mainly the same pressure works on the front side of the sealing in space 23 as well as on the rear side of the same in gap 24.
  • the object of a pressure equilibrium of secondary sealing 18 is partly to lower the wear of the secondary sealing and partly to minimize the frictional forces from the secondary sealing.
  • rinsing water can also be pressed past primary sealing/wiper 17 into the pump housing, at least initially during the pump stroke. In case it is desirable that this rinsing effect is to continue essentially during the entire pump stroke, this can be done by controlling the oil feeding to control cylinder 38 by means of a suitable dimensional restriction in conduit 86A.
  • conduits 82A and 83A which enables driving piston 12A in the A-unit to start its return stroke, position V. Since no work pressure is developed on driving piston 12A in driving chamber 42A, the pressure from conduit 84A, which essentially is obtained from return chamber 43B in the B-unit, will be sufficient to drive back driving piston 12A, the hydraulic medium from driving chamber 42A being drained to sump 70 via conduit 82A, recess 67 and draining conduit 83A.
  • Driving piston 12B moves at an even speed forwards in the same way as driving piston 12A did in the introductory part of the functional description.
  • This phase for driving piston 12B of the B-unit is indicated by the dashed line-drawn, upper, planar curve in the diagram in Fig. 2A.
  • driving piston 12A is driven in the return direction and pulls the plunger along and out of pump housing chamber 5A by means of driving rod 13A.
  • Valve 4A is now closed and fresh pump medium is being sucked into pump housing chamber 5A via valve 3A.
  • This phase continues, until driving piston 12B has advanced so far, that gap 52B has started communicating with conduit 89B and driving piston 12A has reached its upper end position, slide 60 now being able to be pushed to the right, position VIII.
  • Rinsing water is fed by pressure through conduit 32 past nonreturn valve 33, Fig. 1C, and on through rinsing water chamber 34, duct 26, gap 24, conduits 25 and 26, past valve 48 and out through draining conduit 39. Rinsing water chamber 34 is then filled with rinsing water, and at the same time gap 24 between sealing sleeves 18 and 19 is washed clean, possible impurities which come along with plunger 10A past sealing sleeves 17 and 18 being rinsed away from the system.
  • main sealing 17 which in this phase functions as a wiper against the smooth, cylindrical outer side 16 of plunger 10A. Consequently, only insignificant amounts of impurities pass main sealing 17, provided sleeve 17 has not been damaged.
  • FIG. 2B illustrates the corresponding conditions in the suction conduit of the integrated pump assembly.
  • the discontinuous process in the suction conduit is considerably simpler to control and does not influence the even outflow from the pump.
  • the pump characteristic does not have the shape of fully straight lines.
  • the curve is a mainly horizontal curve, the central position of the slide, Fig. 1B, defining a point of inflection on the curve.
  • sealing housing 6A is washed with rinsing water during two phases in each work cycle, it may be desirable to, when the work has been done, carefully clean sealing housing 6A and also pump housing 1A. This is particulary true, if strongly contaminating media have been pumped or media which for some other reason must be removed from the pump is order not to damage it, e.g. cement or other substances, which can harden and in the long run make the pump incapable of functioning.
  • Fig. 3 illustrates how such a rinsing can be done.
  • Two additional conduits 90 and 91 are used for this purpose, which extend through the rinsing water housing wall to annular space 23 in front of secondary sealing sleeve 18 and from annular gap 22 behind main sealing and wiper sleeve 17 respectively.
  • Rinsing water is fed through conduit 90 to annular space 23 and flows through this space on each side of plunger 10A to its opposite side, from which side the water flows through passage 30 on the rear side of guide 20 and into annular gap 22.
  • the water continues through gap 22 and passes again on each side of plunger 10A and is finally evacuated through draining conduit 91. In this way all possible impurities in spaces 22 and 23 are efficiently removed.
  • rinsing water can also be fed through conduit 32 when the pump is inoperative in order to, via rinsing water chamber 34 and conduit 26, also clean gap 24, which is drained through conduit 39 in a way which has been explained in connection with the description of the return stroke of plunger 10A.
  • pump housing chamber 5A can be washed with rinsing water, which is fed through a conduit 92 (possibly through the same conduit as the outlet conduit for the pump medium).
  • a drain plug 93 has in this situation been removed and consequently, the rinsing water can be drained through bottom opening 94.
  • a rinsing water housing 107 designed in the same way as in the previous embodiment, and a modified sealing housing 106 are used.
  • a draining housing and ancillary draining elements are not needed in this embodiment.
  • the sealing housing contains a combined primary sealing and wiper 117, a second rear sealing 119 as well as guides 120 and 121.
  • Sealing housing 106 also contains a non-return valve 100, the counterflow side of which is connected to a gap 122 on the rear side of primary sealing/wiper 117 and to an annular recess 124 between rear sealing 119 and first guide 120.
  • rinsing water chamber 134 is filled with rinsing water, which during the pump stroke is pressed out past valve 100 and into space 124 and gap 122, and in this way, in the same way as in the previous embodiment, impurities are essentially stopped from being pressed upwards past primary sealing/wiper 117 during the pump stroke.
  • no rinsing takes place according to this embodiment.
  • Non-return valve 100 stops during the return stroke possible impurities from passing into rinsing water chamber 134, when the latter is connected to the feed conduit for rinsing water.
  • a pump unit designed for a higher pump medium pressure, i.e. 100-300 bar, will now be explained, reference being made to Fig. 5.
  • This pump unit can also be used for higher pressures than 300 bar, but according to the state of the art there are no hydraulic pumps on the market able to provide a pressure considerably higher than 300 bar, and consequently, 300 bar is a practical upper limit considering the state of the art.
  • Fig. 5 the same numerals are used for elements, which are exactly identical with the elements shown in Fig. 1A. Elements, which have counterparts in Fig. 1A but have been designed in a somewhat different way or which have a slightly different function, have been given the same numerals as in Fig. 1A but with a prime sign.
  • Two pump units of the type shown in Fig. 5 are designed to be integrated into a plunger pump assembly, in the same way as has been described above, a slide valve of the type described above being a part of the system and designed to control the shiftings of the two pump units.
  • a hydraulic assembly H is also in this case a part of the equipment.
  • Each one of the two pump units which are designed in the same way, comprises a pump housing 1, a hydraulic chamber housing 9' and a return unit 2'.
  • Pump housing 1 contains a pump housing chamber 5 with an inlet conduit with a nonreturn valve 3 and an outlet conduit with a nonreturn valve 4.
  • Pump housing 1 is connected to a sealing housing 6 and said hydraulic chamber housing 9'.
  • Sealing housing 6' and hydraulic chamber housing 9' are integrated parts of pump housing 1 and constitute acontinuation of cylinder-shaped pump housing chamber 5 but with smaller inner dimensions.
  • a rinsing water housing 7' is connected to sealing housing 6'.
  • a plunger 10 is used.
  • Return unit 2' comprises the following main elements: a return cylinder 11', a return piston 12', a return piston rod 13', which connects return piston 12' to plunger 10, an end block 14' and a top lid 15'.
  • Elements 1, 6', 7', 9', 11', 14' and 15' are connected to each other by means of bolted joints to one single unit.
  • the unit which comprises plunger 10, return piston 12' and return piston rod 13' is movable between two end positions.
  • Plunger 10 has en even, cylindrical exterior side. It is designed to interact with a number of annular or sleeve-shaped sealings in sealing housing 6', which also is a part of the pump housing cylinder. Close to pump housing chamber 5 there is a first annular element, designed as a metallic rinsing water ring 17', which forms a narrow, gap-shaped rinsing water passage 94 against plunger 10. A first sealing sleeve, which constitutes a combined main sealing and wiper, is designated 18'. A secondary sealing ring 19'seals the spaces between rinsing water and the hydraulic medium, which hydraulic chamber 58' contains. Lower guides between sealing sleeves 17' and 18' are designated 20, and upper guides between sealing ring 18' and hydraulic chamber 58' are designated 21.
  • Elements 17' - 21 are mounted in annular grooves in sealing housing 6. Also, the inner wall of sealing housing 6 has in its cross-section a profile, in which there is an annular space 24', 24a' between primary sealing 17' and secondary sealing 18'. Also, rinsing water ring 17' forms in its upper part an annular space 22' between gap 94 and primary sealing 18'.
  • conduit 26' leads to annular spaces 24', 24a' and from these spaces a conduit 25' leads via a nonreturn valve 28' to an annular groove 25a' in the upper side of rinsing water ring 17'. Groove 25a' communicates via a gap 25b' with space 22'.
  • An inlet conduit 32 for rinsing water extends via a non-return valve 33 into a rinsing water chamber 34, which communicates with above-mentioned conduit 26'.
  • Rinsing water chamber 34 contains a rinsing plunger 35 having a screw-wound return spring 36 on the inner side.
  • a non-return valve 26a' is mounted between rinsing water chamber 34 and conduit 26'.
  • Rinsing plunger 35 can be moved by compressing return spring 36 by means of the hydraulic medium in a control chamber 38'.
  • Control chamber 38' communicates withhydraulic chamber 58' through a conduit 86'.
  • Return piston rod 13' reduces the active surface on plunger 10 on the driving side.
  • the spring constant of return spring 36 is chosen to make rinsing water pressure Pv in rinsing water chamber 33 slightly lower than hydraulic pressure Ph but higher than pump medium pressure Pp during the pump stroke.
  • Unit 2' is designed partly to take care of the return stroke of plunger 10 and partly to guide the movements of plunger 10 in order to make the described pump unit interact with another similar pump unit in the pump assembly according to the movement pattern description in connection with the first embodiment.
  • the slide valve shown in Fig. 1A and Fig. 1B is a very important element in this control function.
  • the slide in this valve can according to the embodiment be moved by means of hydraulic pressure via a conduit 89', which can either work as a draining conduit, as is shown in Fig. 5, or as a control conduit, when piston 12' is in its upper position.
  • the movements of piston 12' are caused by hydraulic oil from a pump through a control conduit 84', which communicates with a return chamber 43'.
  • a draining chamber 42' is located above piston 12' and can be drained through a draining conduit 88'.
  • the hydraulic fluid in hydraulic chamber 58' is fed and drained through a conduit 82'.
  • the hydraulic fluid is directly acting on plunger 10 and not, as in the above-described embodiment, via a driving and return piston.
  • piston 12' works solely as a return and draining piston.
  • For the rest piston 10 follows the same movement progress as has been described above. Thus, only how the rinsing of the sealing elements is done according to this embodiment will be described here in more detail.
  • hydraulic oil is fed through conduit 82' into hydraulic chamber 58' and drives plunger 10 downwards.
  • the hydraulic medium passes from hydraulic chamber 58' on and past guides 21 and conduit 86' into control chamber 38'.
  • Pressure Ph drives rinsing plunger 35' and presses the rinsing water in rinsing water chamber 34' past valve 26a', via conduit 26' and into gap 24' and 24a'. From the latter the rinsing water passes through conduit 25', past valve 28' and into annular groove 25a' in rinsing water ring 17'.
  • the rinsing water passes from this annular space 25a' through gap 25b' into space 22' in front of sealing sleeve 18' and flows out through gap 94 into pump housing chamber 5, plunger 10 being rinsed.
  • Return spring 36 is simultaneously compressed. It has a suitable spring constant and in combination with a suitable surface on rinsing water plunger 35' a rinsing water pressure Pv can be obtained, which is larger than pump pressure Pp in pump housing chamber 5 but smaller than hydraulic pressure Ph during the pump stroke.
  • Valve 33 is opened up instead. Rinsing water plunger 35' is returned by means of return spring 36, and fresh rinsing water flows into rinsing water chamber 33' through conduit 32.
  • the hydraulic medium from control chamber 38' is returned via conduit 86' to hydraulic chamber 58'.
  • Space 22' which is located in rinsing water ring 17' between gap 94 and primary sealing 18', is designed to form a rinsing water buffer between the pump medium and the primary sealing in order to reduce wear and damages to primary sealing/wiper 18'. It is to be noted that during the return stroke nonreturn valve 28' is closed, the rinsing water in spaces 22', 25b' and 25a' remaining during the entire return stroke in the spaces. Even if small amounts of the pump fluid can pass into space 22' during the return stroke, it will be strongly diluted with rinsing water and is washed out during the next pump stroke.

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  • Details Of Reciprocating Pumps (AREA)

Claims (8)

  1. Eine Pumpeinrichtung mit einer ersten und einer zweiten Pumpeinheit (A, B), mit jeweils einer Pumpgehäusekammer (5A, 5B), einem Pumpgehäusezylinder und einem beweglich in dem Pumpgehäusezylinder angeordneten Verdrängungselement, welches während eines Pumphubes in die genannte Pumpgehäusekammer eingetrieben wird; wobei die erste Pumpeinheit (A) weiterhin eine erste Antriebseinheit (2A) für das Verdrängungselement der ersten Pumpeinheit aufweist und die erste Antriebseinheit einen ersten Hydraulikzylinder (11A) mit einem ersten Antriebskolben (12A) in diesem Hydraulikzylinder sowie einer Antriebsstange (13A) aufweist, welche den ersten Antriebskolben mit dem Verdrängungselement verbindet; wobei die zweite Pumpeinheit (B) weiterhin eine zweite Antriebseinheit (12B) für das Verdrängungselement der zweiten Pumpeinheit aufweist und die zweite Antriebseinheit einen zweiten Hydraulikzylinder (11B) mit einem zweiten Antriebskolben (12B) in dem Hydraulikzylinder sowie einer Antriebsstange (13B) aufweist, welche den zweiten Antriebskolben mit dem Verdrängungselement (10B) der zweiten Pumpeinheit verbindet; wobei die Pumpeinrichtung weiterhin eine Druckmittelquelle (70) sowie eine erste Druckpumpe (71) für die Versorgung der ersten und zweiten Pumpeinheit (A, B) mit hydraulischem Medium unter Druck aufweist, gekennzeichnet durch
    - ein gemeinsames Steuerventil (V) für die erste und zweite Pumpeinheit zur Steuerung der Bewegung des Verdrängungselements in der ersten und zweiten Pumpeinheit (A, B), wobei das Steuerventil ein Ventilgehäuse (G) mit ersten und zweiten Endlagen (EA; EB) und einen Schieber (60) aufweist, der Aussparungen (61, 62, 63) besitzt und in dem Ventilgehäuse zwischen den ersten und den zweiten Endlagen und Stellungen dazwischen bewegbar ist, um den Fluß des hydraulischen Mediums von der ersten Druckpumpe (71) zu den ersten und zweiten Hydraulikzylindern (11A, 11B) und von den ersten und zweiten Hydraulikzylindern (11A, 11B) zu der Druckmittelquelle (70) zu regeln,
    - eine hydraulische Hauptleitung (80), welche die erste Druckpumpe (71) mit dem Steuerventil (V) verbindet;
    - eine erste Antriebsleitung (82A), welche das Steuerventil (V) mit einem hinteren Ende des ersten Hydraulikzylinders (11A) verbindet;
    - eine zweite Antriebsleitung (82B), welche das Steuerventil (V) mit einem Ende des zweiten Hydraulikzylinders (11B) verbindet;
    - eine erste Rückholleitung (84A), welche ein vorderes Ende des ersten Hydraulikzylinders (11A) mit der Druckmittelquelle (70) verbindet;
    - eine zweite Rückholleitung (84B), welche ein vorderes Ende des zweiten Hydraulikzylinders (11B) mit der Druckmittelquelle (70) verbindet;
    - eine erste hydraulische Steuerleitung (89A), welche sich zwischen einer ersten Regelleitung (53A) in dem ersten Hydraulikzylinder (11A), die sich in einer Zwischenlage zwischen dem hinteren und dem vorderen Ende des ersten Hydraulikzylinders befindet und einem Anschluß (PA) an eine (EA) der ersten und zweiten Endlagen des Ventilgehäuses erstreckt;
    - eine zweite hydraulische Steuerleitung (89B), welche sich zwischen einer zweiten Regelleitung (53B) in dem zweiten Hydraulikzylinder (11B), die sich in einer Zwischenlage zwischen dem hinteren und dem vorderen Ende des zweiten Hydraulikzylinders befindet und einem Anschluß (PB) an eine (EB) der ersten und zweiten Endlagen des Ventilgehäuses erstreckt;
    - wobei der erste Antriebskolben (12A) eine erste Antriebskolbenleitung (51A) aufweist, welche einen Anschluß (52A) in der Seitenwand des Zylinders des ersten Antriebskolbens (12A) mit einer ersten hydraulischen Abflußleitung (88A) verbindet; und wobei
    - der zweite Antriebskolben (12B) eine zweite Antriebs-kolbenleitung (51B) aufweist, welche einen Anschluß (52B) in der Seitenwand des Zylinders des zweiten Antriebskolbens (12B) mit einer zweiten hydraulischen Abflußleitung (88B) verbindet.
  2. Pumpeinrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß das Steuerventilgehäuse einen mittleren Anschluß (CP), welcher mit der hydraulischen Hauptleitung (80) verbunden ist, einen ersten Anschluß (P1) für die erste Antriebsleitung (82A) auf der einen Seite der mittleren Öffnung und einen zweiten Anschluß (P2) für die zweite Antriebsleitung (82B) auf dessen anderer Seite aufweist, wobei der Schieber (60) eine mittlere Aussparung (66) von einer solchen Länge aufweist, daß die Aussparung in der ersten und zweiten, nicht-mittigen Lage des Schiebers in dem Ventilgehäuse die Hauptleitung (80) mit entweder der ersten oder der zweiten Antriebsleitungen (82A, 82B) über einen der genannten ersten oder zweiten Anschlüsse (P1, P2) verbinden kann, und in einer dritten, mittleren Lage die ersten und zweiten Antriebsleitungen und die Hauptleitungen miteinander über die ersten, zweiten und mittleren Anschlüsse (P1, P2, PC) verbinden kann.
  3. Eine Pumpeinrichtung gemäß Anspruch 2, dadurch gekennzeichnet, daß das Steuerventilgehäuse einen dritten Anschluß (P3) zwischen dem ersten Anschluß (P1) und einem (PA) der Anschlüsse (PA, PB), einen vierten Anschluß (P4) zwischen dem zweiten Anschluß (P2) und den anderen (PB) der Anschlüsse (PA, PB), eine erste Abflußleitung (83A), welche den dritten Anschluß (P3) mit der Druckmittelquelle (70) verbindet, eine zweite Abflußleitung (83B), welche den vierten Anschluß (P4) mit der Druckmittelquelle (70) verbindet, aufweist, wobei der Schieber zwei nicht-zentrale Aussparungen (65, 67) aufweist, wobei jede kürzer als die mittlere Aussparung ist und so an dem Schieber angeordnet ist, daß sie in einer Endlage des Schiebers eine der ersten und zweiten Antriebseinheiten (2A, 2B) mit einer der ersten und zweiten Abflußleitungen, jedoch nicht mit irgendeiner anderen Leitung, verbinden kann.
  4. Eine Pumpeinrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß in jeder der Steuerleitungen eine Drossel (68A, 68B) angeordnet ist.
  5. Eine Pumpeinrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß eine zweite Druckpumpe (72) angeordnet ist, um von der genannten Druckmittelquelle (70) Druckmittel durch die erste und zweite Rückhubleitung (84A, 84B) zu pumpen, was für die ersten und zweiten Antriebskolben (12A, 12B) jeweils zu dem Rückhub führt.
  6. Eine Pumpeinrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß das Verdrängungselement ein Plungerkolben (10A, 10B) ist.
  7. Eine Pumpeinrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß das Verdrängungselement ein Hubkolben ist.
  8. Eine Pumpeinrichtung gemäß Anspruch 1, dadurch gekennzeichnet, daß das Verdrängungselement eine Membrane ist.
EP90915533A 1990-09-05 1990-09-05 Pumpeinheit mit zwei verdrängerpumpen Expired - Lifetime EP0592395B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SE1990/000566 WO1992004543A1 (en) 1990-09-05 1990-09-05 A displacement pump as well as a pump assembly comprising two displacement pumps

Publications (2)

Publication Number Publication Date
EP0592395A1 EP0592395A1 (de) 1994-04-20
EP0592395B1 true EP0592395B1 (de) 1996-08-14

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Application Number Title Priority Date Filing Date
EP90915533A Expired - Lifetime EP0592395B1 (de) 1990-09-05 1990-09-05 Pumpeinheit mit zwei verdrängerpumpen

Country Status (4)

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EP (1) EP0592395B1 (de)
DE (1) DE69028123T2 (de)
SE (1) SE467839B (de)
WO (1) WO1992004543A1 (de)

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE8105988L (sv) * 1981-10-09 1983-04-10 Hk Eng Ab Pump av deplacementtyp

Also Published As

Publication number Publication date
DE69028123D1 (de) 1996-09-19
WO1992004543A1 (en) 1992-03-19
EP0592395A1 (de) 1994-04-20
SE8901213D0 (sv) 1989-04-06
SE8901213L (sv) 1990-10-07
SE467839B (sv) 1992-09-21
DE69028123T2 (de) 1997-01-23

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