EP2483558B1 - Pompe por une appareil de nettoyage haute pression - Google Patents

Pompe por une appareil de nettoyage haute pression Download PDF

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Publication number
EP2483558B1
EP2483558B1 EP10759871.6A EP10759871A EP2483558B1 EP 2483558 B1 EP2483558 B1 EP 2483558B1 EP 10759871 A EP10759871 A EP 10759871A EP 2483558 B1 EP2483558 B1 EP 2483558B1
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EP
European Patent Office
Prior art keywords
pump
pressure
valve
accordance
line
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.)
Active
Application number
EP10759871.6A
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German (de)
English (en)
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EP2483558A1 (fr
Inventor
Robert Nathan
Jürgen Erdmann
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.)
Alfred Kaercher SE and Co KG
Original Assignee
Alfred Kaercher SE and Co KG
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Publication of EP2483558A1 publication Critical patent/EP2483558A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B49/22—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 means of valves
    • F04B49/24—Bypassing
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/143—Cylinders

Definitions

  • the invention relates to a pump for a high-pressure cleaning device for conveying a cleaning liquid with at least one pumping chamber into which at least one reciprocating piston dips and which is connected via at least one inlet valve to a suction line and at least one outlet valve to a pressure line, and with a bypass line leading from the pressure line to the suction line, in which an overflow valve is arranged, whose valve body is connected to a control piston which is displaceably held in a control chamber with the interposition of a sealing element and the valve body in dependence on the flow rate of the cleaning liquid in the pressure line in a closed position or an open position shifts, wherein the control piston, the control chamber in an upstream of a throttle point connected to the pressure line high-pressure chamber and a downstream of the throttle point connected to the pressure line N divided sub-pressure chamber.
  • Such pumps are from the DE 196 07 881 A1 known.
  • a cleaning liquid such as water
  • a cleaning liquid can be pressurized and then directed, for example, via an attachable to the pressure line pressure hose and arranged at the free end of the pressure hose nozzle head to an object.
  • the mechanical load on the pump and heat losses can be reduced, the funded by the pump cleaning liquid is performed with closed nozzle head with the lowest possible flow resistance in the circuit, ie it is returned from the pressure line back to the suction line, so that the pressure in the pressure line lowers.
  • the pressure line is connected via a bypass line to the suction line and in the bypass line an overflow valve is arranged.
  • the overflow valve closes the flow connection between the pressure line and the suction line. If the nozzle head is closed, the overflow valve releases the flow connection between the pressure line and the suction line, so that the pressure prevailing in the pressure line is reduced.
  • the valve body of the overflow valve is connected for this purpose with a control piston which moves the valve body in response to the flow rate of the cleaning liquid in the pressure line in a closed position or an open position. The flow rate of the cleaning liquid in the pressure line depends on whether the nozzle head is open or closed.
  • the control piston is slidably held in the control chamber and divides these into a high-pressure chamber and a low-pressure chamber.
  • the high-pressure chamber is connected to the pressure line upstream of a throttle point
  • the low-pressure chamber is connected to the pressure line downstream of the throttle point.
  • an orifice for example, an injector be arranged in the pressure line, with the aid of a cleaning chemical of the pressurized cleaning liquid can be mixed.
  • the throttle point In the presence of a liquid flow in the pressure line, the throttle point has the consequence that the pressure downstream of the throttle point differs from the pressure upstream of the throttle point.
  • the control piston Since the high-pressure chamber upstream of the throttle point is connected to the pressure line, whereas the low-pressure chamber downstream of the throttle point is in communication with the pressure line, the control piston is subjected to a differential pressure in the presence of a liquid flow in the pressure line. Due to the differential pressure acting on it, the control piston displaces the valve body of the overflow valve counter to the flow direction prevailing in the bypass line into a closed position in which the valve body bears against a valve seat of the overflow valve. If the liquid flow in the pressure line is interrupted, the throttle point causes no pressure drop and the pressure in the low pressure chamber corresponds to the pressure in the high pressure chamber.
  • the control piston causes a tight separation of the high pressure chamber from the low pressure chamber.
  • a sealing element is arranged between the control piston and the control chamber.
  • This pressure difference must reliably withstand the sealing element even after prolonged operation of the pump, because a leaking separation of the low pressure chamber from the high pressure chamber in the region of the control piston can lead to an impairment of the pump.
  • Object of the present invention is to develop a pump of the type mentioned in such a way that it is less prone to failure and can be produced more cheaply.
  • a sliding element is arranged in the control chamber, on which the control piston with the interposition of the sealing element slidably and sealingly abuts.
  • the sliding element in turn is close to the wall of the control chamber.
  • the sliding element may be designed as a smoothing member, on which the control piston along with its surrounding sealing element can slide along while maintaining the seal the low pressure chamber of the high pressure chamber. The sliding element thus forms a sealing surface against which the sealing element slidably rests.
  • the sliding element is preferably made of a plastic material.
  • the wall of the control chamber can be made for example of brass or of an aluminum alloy.
  • the sliding element is made of a POM (polyoxymethylene) or a PTFE (polytetrafluoroethylene) material.
  • POM polyoxymethylene
  • PTFE polytetrafluoroethylene
  • the sliding element is dirt-repellent, d. H. it has only a very low adhesion to dirt particles, oils and fats. As a result, the susceptibility to failure of the pump is kept very low.
  • the sliding element may for example be designed in the form of a coating which covers the wall of the control chamber on the inside.
  • the sliding element is designed as insertable into the control chamber sliding sleeve.
  • the sliding sleeve forms an independently manageable component that can be used in the assembly of the pump in the control chamber.
  • the sliding sleeve can bear on the outside an annular groove in which a sealing ring is arranged. With the help of the externally arranged sealing ring, the sliding sleeve can be applied sealingly against the wall of the control chamber.
  • the sliding sleeve can form a stop, for example a step which limits the range of movement of the control piston in the control chamber.
  • the pump has a rear housing part and a front housing part, which are joined tightly in a joining region, wherein the front housing part comprises a parallel to the pressure line aligned passageway which forms the control chamber, and wherein the sliding element is insertable into the passageway ,
  • the rear housing part faces a drive device of the pump, for example an electric motor. Between the electric motor and the rear housing part, a gear and / or a swash plate and / or a piston guide can be arranged.
  • the front housing part sits on the rear housing part and faces away from the drive device of the pump.
  • the front housing part comprises a parallel to the pressure line aligned passageway. In the passage, the sliding element can be easily used during assembly of the pump, d. H. the installation costs can be kept low.
  • the passageway in alignment with the control chamber forms a portion of the bypass line which opens into a suction line section and receives the overflow valve.
  • the overflow valve is thus arranged in the alignment of the control chamber arranged portion of the bypass line and can be used in the installation of the pump in a similar manner as the sliding member in the axial direction in the passageway.
  • the installation of the pump is characterized particularly simple.
  • the overflow valve has a sleeve-shaped valve housing, which forms a valve seat and can be inserted into the through-channel.
  • the passageway forms a stop for the valve housing of the overflow valve.
  • the sliding element can be inserted into the through-channel, and then then the control piston can be inserted into the sliding element.
  • the sliding element and the sleeve-shaped valve housing of the overflow valve can each be aligned coaxially with the longitudinal axis of the through-channel.
  • a compression spring can be arranged, which is supported on the one hand on the valve housing and on the other hand on the control piston and this acted upon by a restoring force, after he has moved the valve body of the overflow valve in an open position.
  • a shaft which is surrounded by the compression spring and forms a guide element for the compression spring.
  • a particularly simple assembly is achieved in an advantageous embodiment of the pump according to the invention characterized in that the passageway extends from an end face to a rear side of the front housing part and the sliding member and the valve housing are frontally inserted into the passageway.
  • the through-channel can be closed by means of a sealing plug after assembly of the valve housing of the overflow valve and of the sliding element and of the control piston.
  • a suction line section is arranged in the joining region between the two housing parts, into which opening the section of the bypass line which receives the overflow valve.
  • the Saug effetsabites can be made inexpensively before joining the two housing parts in a simple manner. As a result, the manufacturing and assembly costs of the pump can be additionally reduced.
  • the bypass line can be selected very short by the arrangement of the Saug effetsabitess in the joining region between the two housing parts. This has the advantage that the flow losses of the cleaning liquid in the bypass line can be kept low.
  • the arranged between the two housing parts suction line section may have a relatively large flow cross-section. As a result, the flow losses of the cleaning liquid in the circulation operation of the pump can be additionally reduced.
  • the arrangement of the Saug einsabitess in the joining region between the front and the rear housing part has the additional advantage that the geometric shape of the Saug effetsabiteses subject to lower boundary conditions, because before the joining of the two housing parts of the joining area for machining and shaping is directly accessible.
  • Saug effetsabites can therefore, if necessary, a curvy course can be selected, without thereby significantly increasing the production costs.
  • the course of the bypass line can be optimized to the effect that the bypass line has the lowest possible flow resistance and that the spill valve can be used in a simple manner in the bypass line.
  • the suction line section arranged between the two housing parts extends between a first sealing ring and a second sealing ring, which are positioned between the two housing parts.
  • the two sealing rings can not only have the function of sealing the arranged between the two housing parts Saug effetsabgone tight, but they can also take over the function to seal the joint area between the two housing parts.
  • the suction line section extending between the two housing parts forms an outlet section of the suction line.
  • At least one input line may connect to the output section, which receives an inlet valve and leads to a pumping chamber.
  • the bypass line is connected to at least one input line leading to a pumping chamber.
  • the suction line comprises an input section arranged in the front housing part and the suction line section extending in the joining region between the two housing parts forms an output section of the suction line.
  • the inlet section can start from a suction connection of the pump and be aligned, for example, transversely to the pressure line.
  • output section can connect directly.
  • the suction line section running in the joining region is preferably arcuately curved, at least in one section.
  • the arcuate curvature is particularly advantageous in view of the limited space of the pump, because thereby the suction line section receiving spaces for the inlet and outlet valves and for the control piston and, if necessary, the pressure line surrounded. Above all, a circular arc-shaped course of the suction line section arranged in the joining region has proved favorable.
  • the suction line section extending in the joining region is designed as a self-contained ring.
  • an annular space may extend, the said suction line section formed.
  • the annular space can have a relatively large flow cross section, so that the at least one pumping chamber can be supplied with the cleaning fluid to be pumped with low flow resistance.
  • the cleaning liquid can be returned with low flow losses, starting from the pumping chamber via the pressure line, the bypass line and the suction line to the pumping chamber.
  • the front housing part of the pump has a rear parting surface, which is placed with the interposition of at least one sealing element on a front-side parting surface of the rear housing part.
  • a channel is formed in at least one of the parting surfaces, which forms at least a part of the arranged in the joining region between the two housing parts Saug effetsabiteses.
  • the channel is arranged on an outer side of at least one of the housing parts and can thereby be produced very inexpensively.
  • a channel is formed, which is covered by the front-side parting surface of the rear housing part and which forms the arranged in the joining region between the two housing parts Saug effetsabites.
  • the running in the joining region between the two housing parts suction line section engages in an advantageous embodiment of the invention, the pressure line at a distance.
  • the suction line section extending in the joining region surrounds the pressure line in an annular manner.
  • the control piston is connected in an advantageous embodiment via a parallel to the pressure line aligned piston rod with the valve body of the spill valve.
  • a switch plunger may connect to the actuation of a switching element, and in the mouth region between the overflow valve receiving portion of the bypass line and the Saug effetsabites a plunger guide is preferably arranged, against which the switch plunger slidably.
  • the mouth region between the overflow valve receiving portion of the bypass line and arranged in the joining region between the two housing parts Saug effet thus forms a receptacle for a tappet guide on which the switching plunger slidably.
  • the control piston can thus not only move the valve body of the overflow valve but also the switching plunger.
  • the actuatable by the switch plunger switching element for example, a drive device of the pump, preferably an electric motor, on and off.
  • the switch plunger By actuating the switch plunger thus the pump can be activated and deactivated. If the liquid flow is suppressed in the pressure line, the valve body of the overflow valve can pass into its open position and the Wegstö ⁇ el can turn off the pump. If the liquid flow in the pressure line is released again, the valve body of the overflow valve can assume its closed position and the pump can be switched on again by means of the switching plunger. So that the switch plunger does not tilt during its movement, it is slidably against the plunger guide. This is to simplify the installation of the pump in the mouth area between the Bypass line and positioned in the joining region between the two housing parts Saug effetsabites positioned.
  • the plunger guide is designed as a coaxially aligned with the longitudinal axis of the passage channel guide sleeve.
  • the sliding element can be designed in the form of a sliding sleeve and the valve body of the overflow valve can be designed in the form of a valve sleeve.
  • the sliding sleeve, the valve sleeve and the guide sleeve are aligned coaxially to the longitudinal axis of the passage channel of the front housing part, as this, the assembly of the pump can be carried out particularly easily.
  • the tappet guide is preferably arranged in the joining region between the two housing parts.
  • the plunger guide in the assembly of the two housing parts at the back in the front housing part by cross-channel is used.
  • a pump 10 is shown schematically for a high-pressure cleaner.
  • the pump 10 comprises a pump housing 12 with a rear housing part 14 and a front housing part 16.
  • the two housing parts are preferably designed in the form of aluminum die-cast parts.
  • the front housing part 16 is provided with a rear parting surface 20 which is placed on a front side parting surface 22 of the rear housing part 14 with the interposition of an outer sealing ring 24 and an inner sealing ring 26.
  • the two sealing rings 24 and 26 are concentric with each other at the outer or inner edge of a molded into the rear parting surface 20 of the front housing part 16 annular channel 28 is arranged.
  • the annular channel 28 is made in particular FIG. 3 clear. It forms an output section 30 of a suction line, whose input section 32 is formed in the form of a blind hole in the front housing part 16.
  • the rear housing part 14 accommodates pumping chambers 34, in each of which a cylindrical piston 36a or 36b is inserted.
  • the pistons 36a, 36b are through a lip-shaped annular seal 38a and 38b sealed relative to the respective pumping chamber 34.
  • the rear housing part 14 has three pumping chambers, in each of which a piston is immersed. To achieve a better overview, only one pumping chamber 34 and two pistons 36a and 36b are shown in the drawing. All pistons are inserted by a not shown in the drawing, known per se swash plate oscillating in the respective pumping chamber 34 and pulled out by a surrounding the respective piston coil spring 40 back out of the pumping chamber, so that the volume of the pumping chambers 34 changes periodically.
  • Each pumping chamber 34 is in fluid communication with the annular output section 30 of the suction line via an input line 42 into which an inlet valve 44 is inserted.
  • the input line 42 opens into the front-side parting surface 22 of the rear housing part 14. This is for example FIG. 2 clear.
  • each pumping chamber 34 is in flow communication with a longitudinal direction of the pump 10 extending in the front housing part 16 molded pressure line 50.
  • the output line 46 opens into the front-side parting surface 22 of the rear housing part and the pressure line 50 extends from the rear parting surface 20 of the front housing part 16 and extends to a front side 52 of the front housing part 16 facing away from the rear housing part 14.
  • the end face 52 forms the front end of the pump 10.
  • the area between the output lines 46 of the pumping chambers 34 and the pressure line 50 is sealed radially outwardly from the inner sealing ring 26.
  • a central pressure valve 54 is arranged and downstream of the pressure valve 54, the pressure line 50 receives a throttle element in the form of an injector 56. This includes in a conventional manner a first in the flow direction narrowing and then again expanding through-hole 58, from the narrowest point of a transverse bore 60 branches off.
  • Parallel to the pressure line 50 extends from the end face 52 to the rear parting surface 20 a stepped embossed passage 62 through the front housing part 16 therethrough.
  • the end-side end region of the through-channel 62 accommodates a sealing plug 64, which closes off the through-channel 62 on the face side.
  • the through-channel 62 defines a control chamber 66, to which a lower section 70 of a bypass line explained in more detail below connects via a step 68.
  • the lower section 70 receives an overflow valve 72 and opens into the annular channel 28 and thus into the arranged in the joining region between the two housing parts 14, 16 output section 30 of the suction line.
  • the control chamber 66 is cylindrical and receives a sliding member in the form of a sliding sleeve 74 which bears tightly against the wall of the control chamber 66 with the interposition of a sealing ring 76.
  • an actuator in the form of a control piston 78 is held displaceable parallel to the longitudinal axis of the pressure line 50.
  • the control piston 78 divides the control chamber 66 into a low-pressure chamber 80 facing the closure stopper 64 and a high-pressure chamber facing away from the stopper 64 82, which is followed by the lower portion 70 of the bypass line.
  • the control piston On its outer side facing the sliding sleeve, the control piston carries a circumferential annular groove in which a sealing element in the form of a piston sealing ring 81 is arranged.
  • a valve sleeve 86 is inserted with the interposition of a sealing ring 84, which forms a valve housing of the overflow valve 72 and comprises a valve seat 88.
  • a valve body 90 of the spill valve 72 in a closed position, the FIG. 4 is shown, sealing applied.
  • the valve body 90 is formed by a radial extension of a piston rod 92, which extends parallel to the longitudinal axis of the pressure line 50 and is connected with its closure plug 64 facing the end with a molded onto the control piston 78 shaft 94.
  • the piston rod 92 forms a switch plunger 96 which is slidably guided in a plunger guide in the form of a guide sleeve 98 with the interposition of a sealing ring 100.
  • the guide sleeve 98 is arranged in alignment with the valve sleeve 86 of the overflow valve 72 and at a distance therefrom in the annular channel 28 of the rear parting surface 20 of the front housing part 16. The guide sleeve 98 is thus positioned in the mouth region between the overflow valve 72 receiving portion 70 of the bypass line and the output section 30 of the suction line.
  • the switch plunger 96 dips with its free end in a receptacle 102 which is laterally formed in the rear housing part 14 and a known per se and in FIG. 1 dash-dotted illustrated switching element 104 receives, which can be actuated by the switch plunger 96.
  • the switching plunger thus passes through the joining region between the two housing parts 14 and 16.
  • the arranged in the pressure line 50 injector 56 has on its outer side an annular groove 106 into which the transverse bore 60 opens.
  • a control line 108 connects, via which the annular groove 106 is in fluid communication with the low pressure chamber 80.
  • an upper portion 110 of the bypass line Upstream of the injector 56 and the central pressure valve 54 extends from the pressure line 50 to the high-pressure chamber 82, an upper portion 110 of the bypass line. At the upper portion 110 joins in the passage 62, the already mentioned lower portion 70 of the bypass line.
  • the bypass line formed by the two sections 70 and 110 thus defines a flow connection between the pressure line 50 and the outlet section 30 of the suction line. This flow connection can be released and prevented depending on the position of the valve body 90 of the overflow valve 72.
  • a radially arranged high pressure section of the joining region between the two housing parts 14 and 16 is thus surrounded by the annular channel and is sealed relative to the annular channel by means of the inner sealing ring 26.
  • the inner sealing ring 26 separates the radially centrally arranged High pressure portion of the joining region of a ring-shaped low pressure section of the joining region.
  • the low pressure section surrounds the high pressure section. It is designed in the form of the annular channel 28 and sealed radially on the outside by means of the outer sealing ring 24.
  • the pumping chambers 34 can be supplied with cleaning fluid to be delivered via the inlet section 32 and the outlet section 30 of the suction line and the inlet lines 42 adjoining the outlet section 30 in the joining area.
  • the cleaning liquid is pressurized due to the oscillating movement of the pistons 36, and the pressurized liquid is supplied to the pressure line 50 via the output lines 46.
  • the pressurized cleaning fluid flows through the injector 56.
  • the low pressure chamber 80 connected via the control line 108 to the transverse bore 60 is pressurized to a lower pressure than that via the upper section 110 of the bypass line
  • the control piston 78 is displaced in the direction of the closure plug 64, so that the valve body 90 of the overflow valve 72 tightly against the valve seat 88 and thereby the Strömungsverbindu ng between the pressure line 50 and the output section 30 of the suction line is interrupted.
  • the movement of the control piston 78 in the direction of the closure plug 64 is assisted by a compression spring 116, which surrounds the shaft 94 and rests on the one hand on the control piston 78 and on the other hand on the valve sleeve 86
  • the pressure line 50 for example by a nozzle head, which is connected via a pressure hose to the pressure line 50 is closed, resulting in the narrowing of the injector 56 no dynamic pressure reduction, the pressure in this area Rather, the same as the upstream of the pressure valve 54 prevailing pressure.
  • equal pressures result in the low-pressure chamber 80 and the high-pressure chamber 82, and according to a suitable dimension of the effective pressure surfaces of the control piston 78, this is thereby displaced against the action of the compression spring 116 in the direction away from the closure stopper 64.
  • valve body 90 lifts from the valve seat 88, so that the spill valve 72 releases the flow connection from the pressure line 50 via the portions 70 and 110 of the bypass line to the output section 30 of the suction line.
  • the pressure prevailing in the pressure line 50 pressure can be lowered.
  • control piston 78 and the associated piston rod 92 also leads to an actuation of the switching element 104.
  • the drive of the pump 10 can be switched off. An unnecessary operation of the drive with a closed nozzle head is thereby avoided.
  • the movement of the control piston 78 which controls the position of the valve body 90 as well as the position of the switching plunger 96, is very smooth within the sliding sleeve 74.
  • the latter is made of a POM material or of a PTFE material and has with respect to the control piston 78 and the outside of the control piston 78 applied piston sealing ring 81 has a low coefficient of friction. While maintaining its sealing effect, the piston sealing ring 81 together with the control piston 78 in the sliding sleeve 74 parallel to the longitudinal axis of the pressure line 50 back and forth to be shifted depending on the pressure prevailing in the pressure line 50 flow conditions.
  • the installation of the sliding sleeve 74 takes place just as the assembly of the valve sleeve 86 in a simple manner in such a way that the two sleeves 74 and 86 frontally, ie, starting from the end face 52 of the front housing part 16, are inserted into the passageway 62. Subsequently, the compression spring 116 can be inserted into the passage, wherein the compression spring 116 is supported on the valve sleeve 86. In a further assembly step then the control piston 78 and integrally connected to the control piston 78 shaft 94 can be inserted into the passageway 62, the shaft 94 occupies a position within the compression spring 116, and in a subsequent assembly step can then by means of the sealing plug 64 of the Through passage 62 are sealed.
  • the piston rod 92 can then be inserted from the rear parting surface 20 in the passageway 62 and screwed into the shaft 94, and then the guide sleeve 98 can be placed on the switch plunger 96 and inserted into the rear parting surface 20 adjacent end portion of the passageway 62.
  • the spill valve 72 can thus be mounted in the passage 62 as well as the control piston 78 and the sliding sleeve 74 in a simple manner.
  • the two housing parts 14 and 16 can then be joined together with the interposition of the outer and inner sealing rings 24, 26.
  • the two housing parts 14 and 16 can be screwed together, for example by means of clamping screws.

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Claims (13)

  1. Pompe pour appareil de nettoyage à haute pression destinée à refouler un liquide de nettoyage, pourvue d'au moins une chambre (34), dans laquelle s'enfonce au moins un piston (36a, 36b) pouvant être animé d'un mouvement de va-et-vient, et qui est reliée par au moins une soupape d'admission (44) à une conduite d'aspiration (30, 32) et par au moins une soupape d'évacuation (48) à une conduite de refoulement (50), et d'une conduite de dérivation (70, 110) menant de la conduite de refoulement (50) à la conduite d'aspiration (30, 32), conduite de dérivation dans laquelle est disposée une soupape de trop-plein (72) dont le corps (90) est relié à un piston de commande (78), lequel est retenu coulissant dans une chambre de commande (66) avec intercalation d'un élément d'étanchéité (81) et déplace le corps de soupape (90) en fonction du débit du liquide de nettoyage dans la conduite de refoulement (50) dans une position de fermeture ou dans une position d'ouverture, le piston de commande (78) divisant la chambre de commande (66) en une chambre à haute pression (82) reliée en amont d'un point d'étranglement à la conduite de refoulement (50) et en une chambre à basse pression (80) reliée en aval du point d'étranglement à la conduite de refoulement (50), caractérisée en ce qu'un élément coulissant (74) est disposé dans la chambre de commande (66) et repose de manière étanche sur la paroi de la chambre de commande (66), et en ce que le piston de commande (78) est retenu mobile dans l'élément coulissant (74) avec intercalation de l'élément d'étanchéité (81).
  2. Pompe selon la revendication 1, caractérisée en ce que l'élément coulissant (74) est fabriqué en matière plastique.
  3. Pompe selon la revendication 1 ou 2, caractérisée en ce que l'élément coulissant (74) est résistant aux salissures.
  4. Pompe selon la revendication 1, 2 ou 3, caractérisée en ce que l'élément coulissant est réalisé sous la forme d'un manchon coulissant (74) pouvant être inséré dans la chambre de commande (66).
  5. Pompe selon l'une des revendications précédentes, caractérisée en ce que la pompe (10) comprend une partie arrière de carter (14) et une partie avant de carter (16), lesquelles sont assemblées de manière étanche dans une zone d'assemblage, la partie avant de carter (16) présentant un canal de passage (62) orienté parallèlement à la conduite de refoulement (50), lequel canal forme la chambre de commande (66), et l'élément coulissant (74) pouvant être inséré dans le canal de passage (62).
  6. Pompe selon la revendication 5, caractérisée en ce que le canal de passage (62) forme, en alignement avec la chambre de commande (66), un tronçon (70) de la conduite de dérivation, lequel débouche dans une section (30) de la conduite d'aspiration et loge la soupape de trop-plein (72).
  7. Pompe selon la revendication 6, caractérisée en ce que la soupape de trop-plein (72) comprend un carter (86) en forme de manchon, lequel forme un siège de soupape (88) et peut être inséré dans le canal de passage (62).
  8. Pompe selon la revendication 7, caractérisée en ce que le canal de passage (62) s'étend d'une face frontale (52) à une face arrière (20) de la partie avant de carter (16) et en ce que l'élément coulissant (74) et le carter de soupape (86) peuvent être insérés frontalement dans le canal de passage (62).
  9. Pompe selon l'une des revendications 6 à 8, caractérisée en ce que la section de conduite d'aspiration (30) est disposée dans la zone d'assemblage entre les deux parties de carter (14, 16)
  10. Pompe selon la revendication 9, caractérisée en ce que la section de conduite d'aspiration (30) est réalisée sous la forme d'un anneau fermé sur lui-même.
  11. Pompe selon la revendication 9 ou 10, caractérisée en ce que le piston de commande (78) est relié au corps (90) de la soupape par une tige de piston (92) orientée parallèlement à la conduite de refoulement (50), corps auquel se raccorde un poussoir de commutation (96) destiné à actionner un élément de commutation (104), et en ce qu'un guide de poussoir de soupape (98), sur lequel le poussoir de commutation (96) repose de manière coulissante, est disposé dans la zone d'embouchure entre le tronçon (70) de la conduite de dérivation, lequel tronçon loge la soupape de trop-plein (72), et la section de conduite d'aspiration (30).
  12. Pompe selon la revendication 11, caractérisée en ce que le guide de poussoir de soupape est réalisé sous la forme d'un manchon de guidage (98) orienté de manière coaxiale à l'axe longitudinal du canal de passage (62).
  13. Pompe selon la revendication 11 ou 12, caractérisée en ce que le guide de poussoir de soupape (98) est disposé dans la zone d'assemblage entre les deux parties de carter (14, 16).
EP10759871.6A 2009-10-01 2010-09-24 Pompe por une appareil de nettoyage haute pression Active EP2483558B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049095A DE102009049095A1 (de) 2009-10-01 2009-10-01 Pumpe für ein Hochdruckreinigungsgerät
PCT/EP2010/064157 WO2011039115A1 (fr) 2009-10-01 2010-09-24 Pompe pour un appareil de nettoyage à haute pression

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EP2483558A1 EP2483558A1 (fr) 2012-08-08
EP2483558B1 true EP2483558B1 (fr) 2014-07-16

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EP (1) EP2483558B1 (fr)
CN (1) CN102510949B (fr)
DE (1) DE102009049095A1 (fr)
DK (1) DK2483558T3 (fr)
WO (1) WO2011039115A1 (fr)

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CN110832200B (zh) * 2017-06-29 2021-08-10 阿尔弗雷德·卡赫欧洲两合公司 高压清洁设备
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DE102020131796A1 (de) 2020-12-01 2022-06-02 Alfred Kärcher SE & Co. KG Kolbenpumpe für ein hochdruckreinigungsgerät
CN116135350A (zh) * 2021-11-18 2023-05-19 玩艸植造股份有限公司 植物吸管制造设备

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Also Published As

Publication number Publication date
US8568109B2 (en) 2013-10-29
CN102510949B (zh) 2014-10-22
WO2011039115A1 (fr) 2011-04-07
US20120213652A1 (en) 2012-08-23
CN102510949A (zh) 2012-06-20
DE102009049095A1 (de) 2011-04-07
EP2483558A1 (fr) 2012-08-08
DK2483558T3 (da) 2014-09-22

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