EP2483560B1 - Pump for a high-pressure cleaning device - Google Patents

Pump for a high-pressure cleaning device Download PDF

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Publication number
EP2483560B1
EP2483560B1 EP10765399.0A EP10765399A EP2483560B1 EP 2483560 B1 EP2483560 B1 EP 2483560B1 EP 10765399 A EP10765399 A EP 10765399A EP 2483560 B1 EP2483560 B1 EP 2483560B1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
line
accordance
suction 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
EP10765399.0A
Other languages
German (de)
French (fr)
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EP2483560A1 (en
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 date
Application filed by Alfred Kaercher SE and Co KG filed Critical Alfred Kaercher SE and Co KG
Priority to PL10765399T priority Critical patent/PL2483560T3/en
Publication of EP2483560A1 publication Critical patent/EP2483560A1/en
Application granted granted Critical
Publication of EP2483560B1 publication Critical patent/EP2483560B1/en
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Anticipated expiration legal-status Critical

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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
    • F04B49/02—Stopping, starting, unloading or idling control
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/128—Crankcases
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing

Definitions

  • the invention relates to a pump for a high-pressure cleaning device for conveying a cleaning liquid with a pump housing in which at least one pumping chamber is arranged, in which at least one reciprocating piston plunges and the at least one inlet valve with a suction line and at least one outlet valve with a pressure line is connected, and with a leading from the pressure line to the suction line bypass line, in which an overflow valve is arranged, the valve body is connected to an actuator which, depending on the flow rate of the cleaning liquid in the pressure line, the valve body in a closed position or an open position shifts.
  • Such pumps are from the DE 93 01 796 U1 known.
  • a cleaning liquid such as water
  • put under pressure and then be 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 closed operation of the pump does not lead to a continuous high pressure in the pressure line, which has a considerable energy consumption of the pump and considerable heat losses result, usually funded by the pump cleaning fluid is circulated with the lowest possible flow resistance, ie it is returned from the pressure line back to the suction line.
  • 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 In operation of the Pump, ie with the nozzle head open, the overflow valve closes the flow connection between the pressure line and the suction line. In circulation operation, ie with the nozzle head closed, the overflow valve releases the flow connection between the pressure line and the suction line.
  • the overflow valve has a valve body which is connected to an actuator. Depending on the flow rate of the cleaning liquid in the pressure line, the actuator moves the valve body 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. If the nozzle head is closed, the flow rate drops, and this causes the actuator to move the valve body of the spill valve in its open position, so that the pump then goes into circulation operation. If the nozzle head is opened, the flow rate in the pressure line increases and this causes the actuator to move the valve body of the spill valve in the closed position, so that the pump goes into the working mode.
  • Object of the present invention is to develop a pump of the type mentioned in such a way that it can be produced more cost-effectively and manufacturing technology easier.
  • the pump housing has a rear housing part and a front housing part, which are joined together, and that the suction line has a running in the joining region between the two housing parts Saug effetsabites, in which the Bypass line opens.
  • the pump housing comprises a rear and a front housing part.
  • the rear housing part faces a drive device of the pump, for example an electric motor, wherein a transmission and / or a swash plate and a piston guide can be arranged between the electric motor and the rear housing part.
  • the front housing part sits on the rear housing part and faces away from the drive device of the pump.
  • the arrangement of a Saug effetsabitess in the joining region between the front and the rear housing part of the pump housing 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 is directly accessible for machining and shaping.
  • Saug effetsabites therefore a curvy course can be chosen if necessary, without thereby increasing the production costs are significantly increased.
  • the pump according to the invention is therefore particularly suitable for portable high-pressure cleaning devices with relatively low weight.
  • 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 tightly sealing the suction line section arranged between the two housing parts, but they can additionally assume the function of sealing the joining region 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 which receives an input valve and leads to a pump chamber, can connect to the output section.
  • 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 input section can start from a suction connection of the pump and, for example, aligned transversely to the pressure line be.
  • At the input portion of the arranged between the housing parts output section can connect directly.
  • the suction line section running in the joining region is arcuately curved at least in one section.
  • the arcuate curvature is particularly advantageous in view of the limited space in the pump housing, because thereby the suction line section receiving spaces for the inlet and outlet valves and for the actuator and, if necessary, bypass the pressure line.
  • 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 in the joining region between the rear housing part and the front housing part, which forms the said suction line section. This annular space may have a relatively large flow cross-section, so that the at least one pumping space to be pumped cleaning liquid can be supplied with low flow resistance.
  • the front housing part of the pump housing 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 on an outside arranged by 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 forms the arranged in the joining region between the two housing parts Saug effetsabites.
  • a channel is formed, which is covered by the rear parting surface of the front housing part and forms the Saug effetsabites.
  • the running in the joining region between the two housing parts suction line section engages in an advantageous embodiment, the pressure line at a distance.
  • the suction line section extending in the joining region surrounds the pressure line in an annular manner.
  • the actuator is designed as a control piston which divides a control chamber of the front housing part into a low-pressure chamber and a high-pressure chamber, is displaceable in the control chamber and is connected via a piston rod to the valve body of the overflow valve, the low-pressure chamber via a control line is connected downstream of a throttle point with the pressure line and the high-pressure chamber is connected via an upstream of the spill valve arranged portion of the bypass line to the pressure line.
  • a throttle point is arranged in the pressure line of the pump, for example an injector, with its Help a cleaning chemical sucked and can be added to the pressurized cleaning liquid.
  • 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. Since the low-pressure chamber via the control line downstream of the throttle point is in communication with the pressure line, whereas the high-pressure chamber is connected upstream of the throttle point via a portion of the bypass line to the pressure line, the control piston is subjected to a liquid pressure in the presence of a liquid flow through the pressure line with a differential pressure. Due to the differential pressure acting on it, the control piston moves the valve body of the overflow valve counter to the flow direction prevailing in the bypass line into a closed position. If the liquid flow 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.
  • control piston In the absence of a differential pressure between the two chambers, the control piston can be acted upon by a dependent of the pressure surfaces of the two chambers resulting force by which it is displaced in the control chamber such that the valve body connected to it passes into an open position and thereby the flow connection between the pressure line and the suction line releases for a circulation operation of the pump.
  • control piston is transmitted via the piston rod to the valve body.
  • control piston is displaceable parallel to the pressure line and the piston rod is aligned parallel to the pressure line.
  • the piston rod via which the valve body of the overflow valve is connected to the control piston, preferably forms on the side facing away from the control piston of the valve body a switching plunger for actuating a Switching element.
  • the control piston can thereby be used not only for moving the valve body of the overflow valve but also for actuating a switching element.
  • the switching element for example, a drive device of the pump, preferably an electric motor, on and off. By actuating the switch plunger thus the pump can be activated and deactivated. If the fluid flow in the pressure line is prevented in such an embodiment, the overflow valve releases the flow connection between the pressure line and the suction line so that the pressure prevailing in the pressure line can be reduced and the pump is switched off.
  • the pump is restarted when the fluid flow in the pressure line is released again by opening the nozzle head connected to the pressure line, because this lowers the pressure in the low-pressure chamber, with the result that the control piston shifts.
  • This in turn has the consequence that the flow connection between the pressure line and the suction line is interrupted again, and on the other hand, this has the consequence that the pump is turned on again.
  • valve body of the overflow valve is configured in an advantageous embodiment of the invention as a radial extension of the piston rod. This makes it possible to produce the valve body particularly inexpensively.
  • the switching plunger immersed in a preferred embodiment of the invention in a molded-in in the rear housing part recording in which the switching element is arranged.
  • the switching plunger thus passes through the joining region between the two housing parts.
  • bypass line has a section which receives the overflow valve and which intervenes in the region between them in the joining region opens two housing parts extending suction line section and is aligned with the control chamber. Said portion of the bypass line can connect directly to the control chamber.
  • control chamber and the overflow valve receiving portion of the bypass line are aligned parallel to the pressure line.
  • control chamber and the Letstömventil receiving portion of the bypass line are arranged in a passageway which passes through the front housing part from a front end side to a rear parting surface.
  • the longitudinal axis of the through-channel runs parallel to the pressure line.
  • 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 sealed off from the respective pumping chamber 34 by a lip-shaped annular seal 38a or 38b.
  • the rear housing part 14 has three pumping chambers, in each of which a piston is immersed. To achieve a better overview are in the drawing only a pumping chamber 34 and two Pistons 36a and 36b shown. 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 comprises in the usual way a first in the flow direction narrowing and then widening again Through hole 58, from the narrowest point 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 sleeve 74, which rests with the interposition of a sealing ring 76 on the wall of the control chamber 66.
  • 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 82 facing away from the stopper 64, to which the lower portion 70 of the bypass line adjoins.
  • a valve sleeve 86 is inserted with the interposition of a sealing ring 84, which forms a valve seat 88 of the overflow valve 72.
  • 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 surrounded by a radial extension a piston rod 92 is formed, which extends parallel to the longitudinal axis of the pressure line 50 and is connected with its closure plug 64 facing the end with an integrally formed on the control piston 78 shaft 94.
  • the piston rod 92 On the side of the valve body 90 facing away from the shaft 94, the piston rod 92 forms a switch plunger 96, which is slidably guided in 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 switching plunger 96 dives with its free end in a receptacle 102 which is 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 in Depending on the position of the valve body 90 of the overflow valve 72 are released and prevented.
  • 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 centered high-pressure section of the joining region from an annular 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 Pressure line 50 is flowed through with cleaning liquid, thus the lower pressure chamber 80 connected via the control line 108 with the transverse bore 60 is acted upon by a lower pressure than the high pressure chamber connected via the upper portion 110 of the bypass line to the inlet region of the pressure line 50.
  • control piston 78 is displaced in the direction of the closure stopper 64, so that the valve body 90 of the overflow valve 72 bears tightly against the valve seat 88, thereby interrupting the flow connection between the pressure line 50 and the outlet section 30 of the suction line.
  • 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 configuration of the output section 30 of the suction line in the form of the annular channel 28, which is formed in the rear-side parting surface 20 of the front housing part 16, has the advantage that the cleaning liquid in the output section 30 suffers only very small pressure losses.
  • the supply of cleaning fluid to the pumping chambers 34 can thus be carried out with low flow losses.
  • passageway 62 is positioned virtually anywhere on the outside of the pressure line 50 be aligned with the passageway 62 each parallel to the pressure line 50. This gives the designer improved design options and the manufacturing cost of the pump 10 can be kept low.
  • the production of the output section 30 can be relatively easily done on the outside of the front housing part 14, namely in the region of the rear parting surface 20. This allows a further reduction of the manufacturing cost of the pump 10th
  • annular output section 30 Another advantage of the annular output section 30 is that the lower portion 110 of the bypass line can be kept very short. As a result, the pressure loss that suffers the cleaning fluid in the bypass line can be kept low. This in turn has the consequence that the pressure prevailing in the high pressure chamber 82 pressure can be reduced within a very short time in the absence of flow through the pressure line 50 and the overflow valve 72 reliably passes into its open position.

Description

Die Erfindung betrifft eine Pumpe für ein Hochdruckreinigungsgerät zur Förderung einer Reinigungsflüssigkeit mit einem Pumpengehäuse, in dem mindestens eine Pumpkammer angeordnet ist, in die zumindest ein hin- und her bewegbarer Kolben eintaucht und die über mindestens ein Einlassventil mit einer Saugleitung und über mindestens ein Auslassventil mit einer Druckleitung verbunden ist, und mit einer von der Druckleitung zur Saugleitung führenden Bypassleitung, in der ein Überströmventil angeordnet ist, dessen Ventilkörper mit einem Stellglied verbunden ist, das in Abhängigkeit von der Strömungsrate der Reinigungsflüssigkeit in der Druckleitung den Ventilkörper in eine Schließstellung oder eine Offenstellung verschiebt.The invention relates to a pump for a high-pressure cleaning device for conveying a cleaning liquid with a pump housing in which at least one pumping chamber is arranged, in which at least one reciprocating piston plunges and the at least one inlet valve with a suction line and at least one outlet valve with a pressure line is connected, and with a leading from the pressure line to the suction line bypass line, in which an overflow valve is arranged, the valve body is connected to an actuator which, depending on the flow rate of the cleaning liquid in the pressure line, the valve body in a closed position or an open position shifts.

Derartige Pumpen sind aus der DE 93 01 796 U1 bekannt. Mit ihrer Hilfe kann eine Reinigungsflüssigkeit, beispielsweise Wasser, unter Druck gesetzt und anschließend zum Beispiel über einen an die Druckleitung anschließbaren Druckschlauch und einen am freien Ende des Druckschlauches angeordneten Düsenkopf auf einen Gegenstand gerichtet werden. Damit bei verschlossenem Düsenkopf die fortgesetzte Tätigkeit der Pumpe nicht zu einem andauernden hohen Druck in der Druckleitung führt, der einen beträchtlichen Energieverbrauch der Pumpe und erhebliche Wärmeverluste zur Folge hat, wird üblicherweise die von der Pumpe geförderte Reinigungsflüssigkeit mit möglichst geringem Strömungswiderstand im Kreislauf geführt, d. h. sie wird von der Druckleitung wieder zur Saugleitung zurückgeführt. Zu diesem Zweck ist die Druckleitung über eine Bypassleitung mit der Saugleitung verbunden und in der Bypassleitung ist ein Überströmventil angeordnet. Im Arbeitsbetrieb der Pumpe, d. h. bei geöffnetem Düsenkopf, verschließt das Überströmventil die Strömungsverbindung zwischen der Druckleitung und der Saugleitung. Im Kreislaufbetrieb, d. h. bei verschlossenem Düsenkopf, gibt das Überströmventil die Strömungsverbindung zwischen der Druckleitung und der Saugleitung frei. Das Überströmventil weist einen Ventilkörper auf, der mit einem Stellglied verbunden ist. In Abhängigkeit von der Strömungsrate der Reinigungsflüssigkeit in der Druckleitung verschiebt das Stellglied den Ventilkörper in eine Schließstellung oder eine Offenstellung. Die Strömungsrate der Reinigungsflüssigkeit in der Druckleitung ist davon abhängig, ob der Düsenkopf geöffnet oder verschlossen ist. Wird der Düsenkopf verschlossen, so fällt die Strömungsrate ab, und dies veranlasst das Stellglied, den Ventilkörper des Überströmventils in seine Offenstellung zu verschieben, so dass die Pumpe dann in den Kreislaufbetrieb übergeht. Wird der Düsenkopf geöffnet, so erhöht sich die Strömungsrate in der Druckleitung und dies veranlasst das Stellglied, den Ventilkörper des Überströmventils in die Schließstellung zu verschieben, so dass die Pumpe in den Arbeitsbetrieb übergeht.Such pumps are from the DE 93 01 796 U1 known. With their help, a cleaning liquid, such as water, put under pressure and then be 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. Thus, the closed operation of the pump does not lead to a continuous high pressure in the pressure line, which has a considerable energy consumption of the pump and considerable heat losses result, usually funded by the pump cleaning fluid is circulated with the lowest possible flow resistance, ie it is returned from the pressure line back to the suction line. For this purpose, the pressure line is connected via a bypass line to the suction line and in the bypass line an overflow valve is arranged. In operation of the Pump, ie with the nozzle head open, the overflow valve closes the flow connection between the pressure line and the suction line. In circulation operation, ie with the nozzle head closed, the overflow valve releases the flow connection between the pressure line and the suction line. The overflow valve has a valve body which is connected to an actuator. Depending on the flow rate of the cleaning liquid in the pressure line, the actuator moves the valve body 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. If the nozzle head is closed, the flow rate drops, and this causes the actuator to move the valve body of the spill valve in its open position, so that the pump then goes into circulation operation. If the nozzle head is opened, the flow rate in the pressure line increases and this causes the actuator to move the valve body of the spill valve in the closed position, so that the pump goes into the working mode.

Damit derartige Pumpen zur leichteren Handhabung ein möglichst geringes Gewicht aufweisen, wird für die Pumpen eine geringe Baugröße gewählt. Dies führt allerdings im Pumpengehäuse zu beengten Platzverhältnissen. Die Bereitstellung der einzelnen Leitungen und Aufnahmeräume für Ventile ist deshalb häufig fertigungstechnisch schwierig und mit erheblichen Kosten verbunden.In order for such pumps to have the lowest possible weight for easier handling, a small size is selected for the pumps. However, this leads to limited space in the pump housing. The provision of individual lines and receiving spaces for valves is therefore often difficult to manufacture and associated with considerable costs.

Aufgabe der vorliegenden Erfindung ist es, eine Pumpe der eingangs genannten Art derart weiterzubilden, dass sie kostengünstiger und fertigungstechnisch einfacher hergestellt werden kann.Object of the present invention is to develop a pump of the type mentioned in such a way that it can be produced more cost-effectively and manufacturing technology easier.

Diese Aufgabe wird bei einer Pumpe für ein Hochdruckreinigungsgerät der gattungsgemäßen Art erfindungsgemäß dadurch gelöst, dass das Pumpengehäuse ein hinteres Gehäuseteil und ein vorderes Gehäuseteil aufweist, die zusammengefügt sind, und dass die Saugleitung einen im Fügebereich zwischen den beiden Gehäuseteilen verlaufenden Saugleitungsabschnitt aufweist, in den die Bypassleitung einmündet.This object is achieved in a pump for a high-pressure cleaner of the generic type according to the invention that the pump housing has a rear housing part and a front housing part, which are joined together, and that the suction line has a running in the joining region between the two housing parts Saugleitungsabschnitt, in which the Bypass line opens.

Erfindungsgemäß umfasst das Pumpengehäuse ein hinteres und ein vorderes Gehäuseteil. Das hintere Gehäuseteil ist einer Antriebseinrichtung der Pumpe zugewandt, beispielsweise einem Elektromotor, wobei zwischen dem Elektromotor und dem hinteren Gehäuseteil ein Getriebe und/oder eine Taumelscheibe sowie eine Kolbenführung angeordnet sein kann. Das vordere Gehäuseteil sitzt auf dem hinteren Gehäuseteil auf und ist der Antriebseinrichtung der Pumpe abgewandt. Im Fügebereich zwischen den beiden Gehäuseteilen, d. h. in dem Bereich, in dem die beiden Gehäuseteile dicht aneinander liegen, ist gemäß der vorliegenden Erfindung ein Saugleitungsabschnitt angeordnet. Dieser Saugleitungsabschnitt kann vor dem Zusammenfügen der beiden Gehäuseteile auf einfache Weise kostengünstig gefertigt werden und dies wiederum senkt die Herstellungskosten der Pumpe.According to the invention, the pump housing comprises a rear and a front housing part. The rear housing part faces a drive device of the pump, for example an electric motor, wherein a transmission and / or a swash plate and a piston guide can be arranged between the electric motor and the rear housing part. The front housing part sits on the rear housing part and faces away from the drive device of the pump. In the joining area between the two housing parts, d. H. in the region in which the two housing parts are close to each other, a Saugleitungsabschnitt is arranged according to the present invention. This Saugleitungsabschnitt can be made inexpensively before joining the two housing parts in a simple manner and this in turn reduces the cost of manufacturing the pump.

Die Anordnung eines Saugleitungsabschnitts im Fügebereich zwischen dem vorderen und dem hinteren Gehäuseteil des Pumpengehäuses hat darüber hinaus den Vorteil, dass der geometrische Verlauf des Saugleitungsabschnittes geringeren Randbedingungen unterliegt, denn vor dem Zusammenfügen der beiden Gehäuseteile ist der Fügebereich direkt für eine Bearbeitung und Formgebung zugänglich. Für den zwischen den beiden Gehäuseteilen angeordneten Saugleitungsabschnitt kann deshalb bei Bedarf auch ein kurviger Verlauf gewählt werden, ohne dass dadurch die Fertigungskosten wesentlich erhöht werden. Dies wiederum gibt dem Konstrukteur die Möglichkeit, die Anordnung der restlichen Leitungen und Aufnahmeräume des Pumpengehäuses im Hinblick auf eine möglichst geringe Baugröße und einen möglichst geringen Materialeinsatz zu optimieren. Die erfindungsgemäße Pumpe eignet sich daher besonders für tragbare Hochdruckreinigungsgeräte mit verhältnismäßig geringem Gewicht.The arrangement of a Saugleitungsabschnitts in the joining region between the front and the rear housing part of the pump housing has the additional advantage that the geometric shape of the Saugleitungsabschnittes subject to lower boundary conditions, because before the joining of the two housing parts of the joining area is directly accessible for machining and shaping. For the arranged between the two housing parts Saugleitungsabschnitt therefore a curvy course can be chosen if necessary, without thereby increasing the production costs are significantly increased. This, in turn, gives the designer the option of arranging the remaining lines and receiving spaces of the pump housing in terms of the smallest possible size and the lowest possible use of materials to optimize. The pump according to the invention is therefore particularly suitable for portable high-pressure cleaning devices with relatively low weight.

Die Abdichtung des zwischen den beiden Gehäuseteilen verlaufenden Saugleitungsabschnittes kann auf kostengünstige Weise mittels Dichtringe erfolgen, die zwischen den beiden Gehäuseteilen angeordnet sind.The sealing of the running between the two housing parts Saugleitungsabschnittes can be done in a cost effective manner by means of sealing rings, which are arranged between the two housing parts.

Insbesondere kann vorgesehen sein, dass der zwischen den beiden Gehäuseteilen angeordnete Saugleitungsabschnitt zwischen einem ersten Dichtring und einem zweiten Dichtring verläuft, die zwischen den beiden Gehäuseteilen positioniert sind. Die beiden Dichtringe können hierbei nicht nur die Funktion aufweisen, den zwischen den beiden Gehäuseteilen angeordneten Saugleitungsabschnitt dicht zu verschließen, sondern sie können zusätzlich die Funktion übernehmen, den Fügebereich zwischen den beiden Gehäuseteilen abzudichten.In particular, it may be provided that 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. In this case, the two sealing rings can not only have the function of tightly sealing the suction line section arranged between the two housing parts, but they can additionally assume the function of sealing the joining region between the two housing parts.

Von Vorteil ist es, wenn der zwischen den beiden Gehäuseteilen verlaufende Saugleitungsabschnitt einen Ausgangsabschnitt der Saugleitung ausbildet. An den Ausgangsabschnitt kann sich mindestens eine Eingangsleitung anschließen, die ein Eingangsventil aufnimmt und zu einem Pumpraum führt.It is advantageous if the suction line section extending between the two housing parts forms an outlet section of the suction line. At least one input line, which receives an input valve and leads to a pump chamber, can connect to the output section.

Günstigerweise umfasst die Saugleitung einen im vorderen Gehäuseteil angeordneten Eingangsabschnitt und der im Fügebereich zwischen den beiden Gehäuseteilen verlaufende Saugleitungsabschnitt bildet einen Ausgangsabschnitt der Saugleitung. Der Eingangsabschnitt kann von einem Sauganschluss der Pumpe ausgehen und beispielsweise quer zur Druckleitung ausgerichtet sein. An den Eingangsabschnitt kann sich der zwischen den Gehäuseteilen angeordnete Ausgangsabschnitt unmittelbar anschließen.Conveniently, 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 input section can start from a suction connection of the pump and, for example, aligned transversely to the pressure line be. At the input portion of the arranged between the housing parts output section can connect directly.

Von Vorteil ist es, wenn der im Fügebereich verlaufende Saugleitungsabschnitt zumindest in einem Teilstück bogenförmig gekrümmt ist. Die bogenförmige Krümmung ist insbesondere im Hinblick auf die beengten Platzverhältnisse im Pumpengehäuse vorteilhaft, denn dadurch kann der Saugleitungsabschnitt Aufnahmeräume für die Einlass- und Auslassventile und für das Stellglied und bei Bedarf auch die Druckleitung umgehen. Vor allem ein kreisbogenförmiger Verlauf des im Fügebereich angeordneten Saugleitungsabschnittes hat sich als günstig erwiesen.It is advantageous if the suction line section running in the joining region is arcuately curved at least in one section. The arcuate curvature is particularly advantageous in view of the limited space in the pump housing, because thereby the suction line section receiving spaces for the inlet and outlet valves and for the actuator and, if necessary, bypass the pressure line. Above all, a circular arc-shaped course of the suction line section arranged in the joining region has proved favorable.

Bei einer besonders bevorzugten Ausgestaltung der erfindungsgemäßen Pumpe ist der im Fügebereich verlaufende Saugleitungsabschnitt als in sich geschlossener Ring ausgestaltet. Bei einer derartigen Ausführungsform kann sich im Fügebereich zwischen dem hinteren Gehäuseteil und dem vorderen Gehäuseteil ein Ringraum erstrecken, der den genannten Saugleitungsabschnitt ausbildet. Dieser Ringraum kann einen verhältnismäßig großen Strömungsquerschnitt aufweisen, so dass dem mindestens einen Pumpraum die zu fördernde Reinigungsflüssigkeit mit geringem Strömungswiderstand zugeführt werden kann.In a particularly preferred embodiment of the pump according to the invention, the suction line section extending in the joining region is designed as a self-contained ring. In such an embodiment, an annular space may extend in the joining region between the rear housing part and the front housing part, which forms the said suction line section. This annular space may have a relatively large flow cross-section, so that the at least one pumping space to be pumped cleaning liquid can be supplied with low flow resistance.

Das vordere Gehäuseteil des Pumpengehäuses weist eine rückseitige Trennfläche auf, die unter Zwischenlage von mindestens einem Dichtelement auf eine frontseitige Trennfläche des hinteren Gehäuseteils aufgesetzt ist. Bevorzugt ist in mindestens eine der Trennflächen ein Kanal eingeformt, der zumindest ein Teil des im Fügebereich zwischen den beiden Gehäuseteilen angeordneten Saugleitungsabschnittes ausbildet. Der Kanal ist an einer Außenseite von mindestens einem der Gehäuseteile angeordnet und kann dadurch sehr kostengünstig hergestellt werden.The front housing part of the pump housing 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. Preferably, 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 Saugleitungsabschnittes. The channel is on an outside arranged by at least one of the housing parts and can thereby be produced very inexpensively.

Günstig ist es, wenn in die rückseitige Trennfläche des vorderen Gehäuseteils ein Kanal eingeformt ist, der von der frontseitigen Trennfläche des hinteren Gehäuseteils abgedeckt ist und den im Fügebereich zwischen den beiden Gehäuseteilen angeordneten Saugleitungsabschnitt ausbildet.It is advantageous if in the rear parting surface of the front housing part, a channel is formed, which is covered by the front-side parting surface of the rear housing part and forms the arranged in the joining region between the two housing parts Saugleitungsabschnitt.

Alternativ kann beispielsweise vorgesehen sein, dass in die frontseitige Trennfläche des hinteren Gehäuseteils ein Kanal eingeformt ist, der von der rückseitigen Trennfläche des vorderen Gehäuseteils abgedeckt ist und den Saugleitungsabschnitt ausbildet.Alternatively, for example, be provided that in the front-side parting surface of the rear housing part, a channel is formed, which is covered by the rear parting surface of the front housing part and forms the Saugleitungsabschnitt.

Der im Fügebereich zwischen den beiden Gehäuseteilen verlaufende Saugleitungsabschnitt umgreift bei einer vorteilhaften Ausführungsform die Druckleitung in einem Abstand. Insbesondere kann vorgesehen sein, dass der im Fügebereich verlaufende Saugleitungsabschnitt die Druckleitung ringförmig umgibt.The running in the joining region between the two housing parts suction line section engages in an advantageous embodiment, the pressure line at a distance. In particular, it may be provided that the suction line section extending in the joining region surrounds the pressure line in an annular manner.

Das Stellglied ist bei einer vorteilhaften Ausführungsform der Erfindung als Steuerkolben ausgestaltet, der eine Steuerkammer des vorderen Gehäuseteils in eine Niederdruckkammer und eine Hochdruckkammer unterteilt, in der Steuerkammer verschiebbar ist und über eine Kolbenstange mit dem Ventilkörper des Überströmventils verbunden ist, wobei die Niederdruckkammer über eine Steuerleitung stromabwärts einer Drosselstelle mit der Druckleitung verbunden ist und die Hochdruckkammer über ein stromaufwärts des Überströmventils angeordnetes Teilstück der Bypassleitung mit der Druckleitung verbunden ist. Bei einer derartigen Ausgestaltung ist in der Druckleitung der Pumpe eine Drosselstelle angeordnet, beispielsweise ein Injektor, mit dessen Hilfe eine Reinigungschemikalie angesaugt und der unter Druck stehenden Reinigungsflüssigkeit beigemischt werden kann. Bei Vorliegen einer Flüssigkeitsströmung in der Druckleitung hat die Drosselstelle zur Folge, dass sich der Druck stromabwärts der Drosselstelle vom Druck stromaufwärts der Drosselstelle unterscheidet. Da die Niederdruckkammer über die Steuerleitung stromabwärts der Drosselstelle mit der Druckleitung in Verbindung steht, wohingegen die Hochdruckkammer stromaufwärts der Drosselstelle über ein Teilstück der Bypassleitung mit der Druckleitung verbunden ist, wird der Steuerkolben bei Vorliegen einer Flüssigkeitsströmung durch die Druckleitung mit einem Differenzdruck beaufschlagt. Aufgrund des auf ihn einwirkenden Differenzdruckes verschiebt der Steuerkolben den Ventilkörper des Überströmventils entgegen der in der Bypassleitung herrschenden Strömungsrichtung in eine Schließstellung. Wird die Flüssigkeitsströmung unterbrochen, so bewirkt die Drosselstelle keinen Druckabfall und der Druck in der Niederdruckkammer entspricht dem Druck in der Hochdruckkammer. Bei Fehlen eines Differenzdruckes zwischen den beiden Kammern kann der Steuerkolben mit einer von den Druckflächen der beiden Kammern abhängigen resultierenden Kraft beaufschlagt werden, durch die er in der Steuerkammer derart verschoben wird, dass der mit ihm verbundene Ventilkörper in eine Offenstellung übergeht und dadurch die Strömungsverbindung zwischen der Druckleitung und der Saugleitung freigibt für einen Kreislaufbetrieb der Pumpe.In an advantageous embodiment of the invention, the actuator is designed as a control piston which divides a control chamber of the front housing part into a low-pressure chamber and a high-pressure chamber, is displaceable in the control chamber and is connected via a piston rod to the valve body of the overflow valve, the low-pressure chamber via a control line is connected downstream of a throttle point with the pressure line and the high-pressure chamber is connected via an upstream of the spill valve arranged portion of the bypass line to the pressure line. In such an embodiment, a throttle point is arranged in the pressure line of the pump, for example an injector, with its Help a cleaning chemical sucked and can be added to the pressurized cleaning liquid. 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. Since the low-pressure chamber via the control line downstream of the throttle point is in communication with the pressure line, whereas the high-pressure chamber is connected upstream of the throttle point via a portion of the bypass line to the pressure line, the control piston is subjected to a liquid pressure in the presence of a liquid flow through the pressure line with a differential pressure. Due to the differential pressure acting on it, the control piston moves the valve body of the overflow valve counter to the flow direction prevailing in the bypass line into a closed position. If the liquid flow 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. In the absence of a differential pressure between the two chambers, the control piston can be acted upon by a dependent of the pressure surfaces of the two chambers resulting force by which it is displaced in the control chamber such that the valve body connected to it passes into an open position and thereby the flow connection between the pressure line and the suction line releases for a circulation operation of the pump.

Die Bewegung des Steuerkolbens wird über die Kolbenstange auf den Ventilkörper übertragen. Bevorzugt ist der Steuerkolben parallel zur Druckleitung verschiebbar und die Kolbenstange ist parallel zur Druckleitung ausgerichtet.The movement of the control piston is transmitted via the piston rod to the valve body. Preferably, the control piston is displaceable parallel to the pressure line and the piston rod is aligned parallel to the pressure line.

Die Kolbenstange, über die der Ventilkörper des Überströmventils mit dem Steuerkolben verbunden ist, bildet auf der dem Steuerkolben abgewandten Seite des Ventilkörpers bevorzugt einen Schaltstößel aus zur Betätigung eines Schaltelementes. Der Steuerkolben kann dadurch nicht nur zum Verschieben des Ventilkörpers des Überströmventils herangezogen werden sondern auch zur Betätigung eines Schaltelementes. Das Schaltelement kann beispielsweise eine Antriebseinrichtung der Pumpe, vorzugsweise einen Elektromotor, ein- und ausschalten. Durch Betätigung des Schaltstößels kann somit die Pumpe aktiviert und deaktiviert werden. Wird bei einer derartigen Ausgestaltung die Flüssigkeitsströmung in der Druckleitung unterbunden, so gibt zum einen das Überströmventil die Strömungsverbindung zwischen der Druckleitung und der Saugleitung frei, so dass der in der Druckleitung herrschende Druck reduziert werden kann, und zum anderen wird die Pumpe abgeschaltet. Die Wiederinbetriebnahme der Pumpe erfolgt, wenn durch Öffnen des an die Druckleitung angeschlossenen Düsenkopfs die Flüssigkeitsströmung in der Druckleitung wieder freigegeben wird, denn dadurch senkt sich der Druck in der Niederdruckkammer, was zur Folge hat, dass sich der Steuerkolben verschiebt. Dies wiederum hat zum einen zur Folge, dass die Strömungsverbindung zwischen der Druckleitung und der Saugleitung wieder unterbrochen wird, und zum anderen hat dies zur Folge, dass die Pumpe wieder eingeschaltet wird.The piston rod, via which the valve body of the overflow valve is connected to the control piston, preferably forms on the side facing away from the control piston of the valve body a switching plunger for actuating a Switching element. The control piston can thereby be used not only for moving the valve body of the overflow valve but also for actuating a switching element. The switching element, for example, a drive device of the pump, preferably an electric motor, on and off. By actuating the switch plunger thus the pump can be activated and deactivated. If the fluid flow in the pressure line is prevented in such an embodiment, the overflow valve releases the flow connection between the pressure line and the suction line so that the pressure prevailing in the pressure line can be reduced and the pump is switched off. The pump is restarted when the fluid flow in the pressure line is released again by opening the nozzle head connected to the pressure line, because this lowers the pressure in the low-pressure chamber, with the result that the control piston shifts. This in turn has the consequence that the flow connection between the pressure line and the suction line is interrupted again, and on the other hand, this has the consequence that the pump is turned on again.

Der Ventilkörper des Überströmventils ist bei einer vorteilhaften Ausführungsform der Erfindung als radiale Erweiterung der Kolbenstange ausgestaltet. Dies ermöglicht es, den Ventilkörper besonders kostengünstig herzustellen.The valve body of the overflow valve is configured in an advantageous embodiment of the invention as a radial extension of the piston rod. This makes it possible to produce the valve body particularly inexpensively.

Der Schaltstößel taucht bei einer bevorzugten Ausgestaltung der Erfindung in eine in das hintere Gehäuseteil eingeformte Aufnahme ein, in der das Schaltelement angeordnet ist. Der Schaltstößel durchgreift somit den Fügebereich zwischen den beiden Gehäuseteilen.The switching plunger immersed in a preferred embodiment of the invention in a molded-in in the rear housing part recording in which the switching element is arranged. The switching plunger thus passes through the joining region between the two housing parts.

Von besonderem Vorteil ist es, wenn die Bypassleitung ein das Überströmventil aufnehmendes Teilstück aufweist, das in den im Fügebereich zwischen den beiden Gehäuseteilen verlaufenden Saugleitungsabschnitt einmündet und fluchtend zur Steuerkammer ausgerichtet ist. Das genannte Teilstück der Bypassleitung kann sich unmittelbar an die Steuerkammer anschließen.It is particularly advantageous if the bypass line has a section which receives the overflow valve and which intervenes in the region between them in the joining region opens two housing parts extending suction line section and is aligned with the control chamber. Said portion of the bypass line can connect directly to the control chamber.

Günstigerweise sind die Steuerkammer und das das Überströmventil aufnehmende Teilstück der Bypassleitung parallel zur Druckleitung ausgerichtet.Conveniently, the control chamber and the overflow valve receiving portion of the bypass line are aligned parallel to the pressure line.

Bei einer vorteilhaften Ausgestaltung der erfindungsgemäßen Pumpe sind die Steuerkammer und das das Überstömventil aufnehmende Teilstück der Bypassleitung in einem Durchgangskanal angeordnet, der das vordere Gehäuseteil von einer vorderen Stirnseite bis zu einer rückseitigen Trennfläche durchgreift.In an advantageous embodiment of the pump according to the invention, the control chamber and the Überstömventil receiving portion of the bypass line are arranged in a passageway which passes through the front housing part from a front end side to a rear parting surface.

Vorzugsweise verläuft die Längsachse des Durchgangskanals parallel zur Druckleitung.Preferably, the longitudinal axis of the through-channel runs parallel to the pressure line.

Die nachfolgende Beschreibung einer bevorzugten Ausführungsform der Erfindung dient im Zusammenhang mit der Zeichnung der näheren Erläuterung. Es zeigen:

Figur 1:
einen Längsschnitt einer erfindungsgemäßen Pumpe;
Figur 2:
eine perspektivische, in einem vorderen Gehäuseteil teilweise geschnittene Darstellung der Pumpe aus Figur 1 schräg von vorne;
Figur 3:
eine perspektivische, in einem hinteren Gehäuseteil teilweise geschnittene Darstellung der Pumpe aus Figur 1 schräg von hinten;
Figur 4:
eine vergrößerte Schnittdarstellung der Pumpe aus Figur 1 im Bereich eines Überströmventils, dessen Ventilkörper eine Schließstellung einnimmt und
Figur 5:
eine vergrößerte Schnittdarstellung der Pumpe aus Figur 1 im Bereich des Überströmventils, wobei dessen Ventilkörper eine Offenstellung einnimmt.
The following description of a preferred embodiment of the invention serves in conjunction with the drawings for further explanation. Show it:
FIG. 1:
a longitudinal section of a pump according to the invention;
FIG. 2:
a perspective, partially cut in a front housing part representation of the pump FIG. 1 diagonally from the front;
FIG. 3:
a perspective, partially cut in a rear housing part representation of the pump FIG. 1 diagonally from behind;
FIG. 4:
an enlarged sectional view of the pump FIG. 1 in the region of an overflow valve whose valve body assumes a closed position and
FIG. 5:
an enlarged sectional view of the pump FIG. 1 in the region of the overflow valve, wherein the valve body assumes an open position.

In der Zeichnung ist schematisch eine Pumpe 10 für ein Hochdruckreinigungsgerät dargestellt. Die Pumpe 10 umfasst ein Pumpengehäuse 12 mit einem hinteren Gehäuseteil 14 und einem vorderen Gehäuseteil 16. Die beiden Gehäuseteile sind bevorzugt in Form von Aluminium-Druckgussteilen ausgestaltet. Das vordere Gehäuseteil 16 ist mit einer rückseitigen Trennfläche 20 versehen, die auf eine frontseitige Trennfläche 22 des hinteren Gehäuseteils 14 aufgesetzt ist unter Zwischenlage eines äußeren Dichtringes 24 und eines inneren Dichtringes 26. Die beiden Dichtringe 24 und 26 sind konzentrisch zueinander am äußeren bzw. am inneren Rand eines in die rückseitige Trennfläche 20 des vorderen Gehäuseteiles 16 eingeformten Ringkanals 28 angeordnet. Der Ringkanal 28 wird insbesondere aus Figur 3 deutlich. Er bildet einen Ausgangsabschnitt 30 einer Saugleitung, deren Eingangsabschnitt 32 in Form eines Sackloches in das vordere Gehäuseteil 16 eingeformt ist.In the drawing, 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.

Das hintere Gehäuseteil 14 nimmt Pumpkammern 34 auf, in die jeweils ein zylindrischer Kolben 36a bzw. 36b eintaucht. Die Kolben 36a, 36b sind durch eine lippenförmige Ringdichtung 38a bzw. 38b gegenüber der jeweiligen Pumpkammer 34 abgedichtet. Insgesamt weist das hintere Gehäuseteil 14 drei Pumpkammern auf, in die jeweils ein Kolben eintaucht. Zur Erzielung einer besseren Übersicht sind in der Zeichnung nur eine Pumpkammer 34 und zwei Kolben 36a und 36b dargestellt. Sämtliche Kolben werden durch eine in der Zeichnung nicht dargestellte, an sich bekannte Taumelscheibe oszillierend in die jeweilige Pumpkammer 34 eingeschoben und durch eine den jeweiligen Kolben umgebende Schraubenfeder 40 wieder aus der Pumpkammer herausgezogen, so dass sich das Volumen der Pumpkammern 34 periodisch ändert.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 sealed off from the respective pumping chamber 34 by a lip-shaped annular seal 38a or 38b. Overall, the rear housing part 14 has three pumping chambers, in each of which a piston is immersed. To achieve a better overview are in the drawing only a pumping chamber 34 and two Pistons 36a and 36b shown. 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.

Jede Pumpkammer 34 steht über eine Eingangsleitung 42, in die ein Einlassventil 44 eingesetzt ist, mit dem ringförmigen Ausgangsabschnitt 30 der Saugleitung in Strömungsverbindung. Hierzu mündet die Eingangsleitung 42 in die frontseitige Trennfläche 22 des hinteren Gehäuseteils 14. Dies wird beispielsweise aus Figur 2 deutlich.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. For this purpose, 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.

Über eine Ausgangsleitung 46, in die ein Auslassventil 48 eingesetzt ist, steht jede Pumpkammer 34 mit einer in Längsrichtung der Pumpe 10 verlaufenden, in das vordere Gehäuseteil 16 eingeformten Druckleitung 50 in Strömungsverbindung. Die Ausgangsleitung 46 mündet hierzu in die frontseitige Trennfläche 22 des hinteren Gehäuseteils und die Druckleitung 50 geht von der rückseitigen Trennfläche 20 des vorderen Gehäuseteiles 16 aus und erstreckt sich bis zu einer dem hinteren Gehäuseteil 14 abgewandten Stirnseite 52 des vorderen Gehäuseteils 16. Die Stirnseite 52 bildet das vordere Ende der Pumpe 10. Der Bereich zwischen den Ausgangsleitungen 46 der Pumpkammern 34 und der Druckleitung 50 wird radial nach außen vom inneren Dichtring 26 abgedichtet.Via an outlet line 46 into which an outlet valve 48 is inserted, 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. For this purpose, 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.

In der Druckleitung 50 ist ein zentrales Druckventil 54 angeordnet und stromabwärts des Druckventiles 54 nimmt die Druckleitung 50 ein Drosselelement in Form eines Injektors 56 auf. Dieser umfasst in üblicher Weise eine sich in Strömungsrichtung zunächst verengende und sich anschließend wieder erweiternde Durchgangsbohrung 58, von deren engster Stelle eine Querbohrung 60 abzweigt.In the pressure line 50, 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 comprises in the usual way a first in the flow direction narrowing and then widening again Through hole 58, from the narrowest point a transverse bore 60 branches off.

Parallel zur Druckleitung 50 erstreckt sich von der Stirnseite 52 bis zur rückseitigen Trennfläche 20 ein stufig ausgestalteter Durchgangskanal 62 durch das vordere Gehäuseteil 16 hindurch. Der stirnseitige Endbereich des Durchgangskanals 62 nimmt einen Verschlussstopfen 64 auf, der den Durchgangskanal 62 stirnseitig dicht verschließt. In dem sich an den Verschlussstopfen 64 anschließenden Bereich definiert der Durchgangskanal 62 eine Steuerkammer 66, an die sich über eine Stufe 68 ein unteres Teilstück 70 einer nachfolgend näher erläuterten Bypassleitung anschließt. Das untere Teilstück 70 nimmt ein Überströmventil 72 auf und mündet in den Ringkanal 28 und damit in den im Fügebereich zwischen den beiden Gehäuseteilen 14, 16 angeordneten Ausgangsabschnitt 30 der Saugleitung.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. In the region adjoining the sealing plug 64, 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.

Die Steuerkammer 66 ist zylindrisch ausgebildet und nimmt eine Gleithülse 74 auf, die unter Zwischenlage eines Dichtringes 76 an der Wand der Steuerkammer 66 anliegt. In der Gleithülse 74 ist ein Stellglied in Form eines Steuerkolbens 78 parallel zur Längsachse der Druckleitung 50 verschiebbar gehalten. Der Steuerkolben 78 unterteilt die Steuerkammer 66 in eine dem Verschlussstopfen 64 zugewandte Niederdruckkammer 80 und eine dem Verschlussstopfen 64 abgewandte Hochdruckkammer 82, an die sich das untere Teilstück 70 der Bypassleitung anschließt.The control chamber 66 is cylindrical and receives a sliding sleeve 74, which rests with the interposition of a sealing ring 76 on the wall of the control chamber 66. In the sliding sleeve 74, 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 82 facing away from the stopper 64, to which the lower portion 70 of the bypass line adjoins.

In das untere Teilstück 70 der Bypassleitung ist unter Zwischenlage eines Dichtringes 84 eine Ventilhülse 86 eingesetzt, die einen Ventilsitz 88 des Überströmventils 72 ausbildet. An den Ventilsitz 88 ist ein Ventilkörper 90 des Überströmventils 72 in einer Schließstellung, die in Figur 4 dargestellt ist, dichtend anlegbar. Der Ventilkörper 90 wird von einer radialen Erweiterung einer Kolbenstange 92 gebildet, die sich parallel zur Längsachse der Druckleitung 50 erstreckt und mit ihrem dem Verschlussstopfen 64 zugewandten Ende mit einem an den Steuerkolben 78 angeformten Schaft 94 verbunden ist.In the lower portion 70 of the bypass line, a valve sleeve 86 is inserted with the interposition of a sealing ring 84, which forms a valve seat 88 of the overflow valve 72. To the valve seat 88 is 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 surrounded by a radial extension a piston rod 92 is formed, which extends parallel to the longitudinal axis of the pressure line 50 and is connected with its closure plug 64 facing the end with an integrally formed on the control piston 78 shaft 94.

Auf der dem Schaft 94 abgewandten Seite des Ventilkörpers 90 bildet die Kolbenstange 92 einen Schaltstößel 96, der in einer Führungshülse 98 unter Zwischenlage eines Dichtringes 100 gleitend geführt ist. Die Führungshülse 98 ist fluchtend zur Ventilhülse 86 des Überströmventils 72 und im Abstand zu dieser im Ringkanal 28 der rückseitigen Trennfläche 20 des vorderen Gehäuseteils 16 angeordnet.On the side of the valve body 90 facing away from the shaft 94, the piston rod 92 forms a switch plunger 96, which is slidably guided in 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.

Der Schaltstößel 96 taucht mit seinem freien Ende in eine Aufnahme 102 ein, die in das hintere Gehäuseteil 14 eingeformt ist und die ein an sich bekanntes und in Figur 1 strichpunktiert dargestelltes Schaltelement 104 aufnimmt, das vom Schaltstößel 96 betätigt werden kann. Der Schaltstößel durchgreift somit den Fügebereich zwischen den beiden Gehäuseteilen 14 und 16.The switching plunger 96 dives with its free end in a receptacle 102 which is 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.

Der in der Druckleitung 50 angeordnete Injektor 56 weist auf seiner Außenseite eine Ringnut 106 auf, in die die Querbohrung 60 einmündet. An die Ringnut 106 schließt sich eine Steuerleitung 108 an, über die die Ringnut 106 mit der Niederdruckkammer 80 in Strömungsverbindung steht.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. At the annular groove 106, a control line 108 connects, via which the annular groove 106 is in fluid communication with the low pressure chamber 80.

Stromaufwärts des Injektors 56 und des zentralen Druckventils 54 erstreckt sich von der Druckleitung 50 zur Hochdruckkammer 82 ein oberes Teilstück 110 der Bypassleitung. An das obere Teilstück 110 schließt sich im Durchgangskanal 62 das bereits erwähnte untere Teilstück 70 der Bypassleitung an. Die von den beiden Teilstücken 70 und 110 gebildete Bypassleitung definiert somit eine Strömungsverbindung zwischen der Druckleitung 50 und dem Ausgangsabschnitt 30 der Saugleitung. Diese Strömungsverbindung kann in Abhängigkeit von der Stellung des Ventilkörpers 90 des Überströmventils 72 freigegeben und unterbunden werden.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 in Depending on the position of the valve body 90 of the overflow valve 72 are released and prevented.

Wie insbesondere aus Figur 2 deutlich wird, umgibt der Ringkanal 28 und damit der Ausgangsabschnitt 30 der Saugleitung sowohl die Druckleitung 50 als auch sämtliche Ausgangsleitungen 46 der einzelnen Pumpkammern 34 in Umfangsrichtung. Ein radial mittig angeordneter Hochdruckabschnitt des Fügebereichs zwischen den beiden Gehäuseteilen 14 und 16 ist somit vom Ringkanal umgeben und wird gegenüber dem Ringkanal mittels des inneren Dichtrings 26 abgedichtet. Der innere Dichtring 26 trennt den radial mittig angeordneten Hochdruckabschnitt des Fügebereichs von einem ringförmigen Niederdruckabschnitt des Fügebereichs. Der Niederdruckabschnitt umgibt den Hochdruckabschnitt. Er ist in Form des Ringkanals 28 ausgebildet und radial außenseitig mittels des äußeren Dichtrings 24 abgedichtet.As in particular from FIG. 2 becomes clear, surrounds the annular channel 28 and thus the output section 30 of the suction line both the pressure line 50 and all output lines 46 of the individual pumping chambers 34 in the circumferential direction. 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 centered high-pressure section of the joining region from an annular 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.

Über den Eingangsabschnitt 32 und den Ausgangsabschnitt 30 der Saugleitung und die sich im Fügebereich an den Ausgangsabschnitt 30 anschließenden Eingangsleitungen 42 können die Pumpkammern 34 mit zu fördernder Reinigungsflüssigkeit versorgt werden. In den Pumpkammern 34 wird die Reinigungsflüssigkeit aufgrund der oszillierenden Bewegung der Kolben 36 unter Druck gesetzt, und über die Ausgangsleitungen 46 wird die unter Druck gesetzte Flüssigkeit der Druckleitung 50 zugeführt.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. In the pumping chambers 34, 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.

Im normalen Betrieb der Pumpe 10 durchströmt die unter Druck gesetzte Reinigungsflüssigkeit den Injektor 56. Dieser bildet in der Druckleitung 50 eine Drosselstelle, an der die durchströmende Reinigungsflüssigkeit eine Druckabsenkung erleidet, so dass der stromaufwärts des Injektors 56 angeordnete Bereich der Druckleitung 50 einen höheren Druck aufweist als der Bereich der Druckleitung in Höhe der Querbohrung 60 des Injektors 56. Solange die Druckleitung 50 mit Reinigungsflüssigkeit durchströmt wird, wird somit die über die Steuerleitung 108 mit der Querbohrung 60 verbundene Niederdruckkammer 80 mit einem geringeren Druck beaufschlagt als die über das obere Teilstück 110 der Bypassleitung mit dem Eintrittsbereich der Druckleitung 50 verbundene Hochdruckkammer 82. Dies hat zur Folge, dass der Steuerkolben 78 in Richtung des Verschlussstopfens 64 verschoben wird, so dass der Ventilkörper 90 des Überströmventils 72 am Ventilsitz 88 dicht anliegt und dadurch die Strömungsverbindung zwischen der Druckleitung 50 und dem Ausgangsabschnitt 30 der Saugleitung unterbrochen ist. Die Bewegung des Steuerkolbens 78 in Richtung des Verschlussstopfens 64 wird von einer Druckfeder 116 unterstützt, die den Schaft 94 umgibt und einerseits am Steuerkolben 78 und andererseits an der Ventilhülse 86 anliegt.In normal operation of the pump 10, the pressurized cleaning fluid flows through the injector 56. This forms in the pressure line 50, a throttle point at which the flowing cleaning fluid suffers a pressure drop, so that the upstream of the injector 56 arranged region of the pressure line 50 has a higher pressure as the area of the pressure line at the level of the transverse bore 60 of the injector 56. As long as the Pressure line 50 is flowed through with cleaning liquid, thus the lower pressure chamber 80 connected via the control line 108 with the transverse bore 60 is acted upon by a lower pressure than the high pressure chamber connected via the upper portion 110 of the bypass line to the inlet region of the pressure line 50. This has the consequence in that the control piston 78 is displaced in the direction of the closure stopper 64, so that the valve body 90 of the overflow valve 72 bears tightly against the valve seat 88, thereby interrupting the flow connection between the pressure line 50 and the outlet section 30 of the suction line. 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.

Wird die Strömung der Reinigungsflüssigkeit durch die Druckleitung 50 unterbrochen, beispielsweise indem ein Düsenkopf, der über einen Druckschlauch an die Druckleitung 50 angeschlossen ist, verschlossen wird, so ergibt sich im Bereich der Verengung des Injektors 56 keine dynamische Druckabsenkung, der Druck in diesem Bereich ist vielmehr gleich wie der stromaufwärts des Druckventils 54 herrschende Druck. In diesem Falle ergeben sich in der Niederdruckkammer 80 und der Hochdruckkammer 82 gleiche Drücke, und entsprechend einer geeigneten Abmessung der wirksamen Druckflächen des Steuerkolbens 78 wird dieser dadurch entgegen der Wirkung der Druckfeder 116 in die dem Verschlussstopfen 64 abgewandte Richtung verschoben. Folglich hebt der Ventilkörper 90 vom Ventilsitz 88 ab, so dass das Überströmventil 72 die Strömungsverbindung von der Druckleitung 50 über die Teilstücke 70 und 110 der Bypassleitung zum Ausgangsabschnitt 30 der Saugleitung freigibt. Dadurch kann der in der Druckleitung 50 herrschende Druck abgesenkt werden.If the flow of the cleaning liquid is interrupted by 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. In this case, 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. Consequently, the 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. As a result, the pressure prevailing in the pressure line 50 pressure can be lowered.

Die Bewegung des Steuerkolbens 78 und der mit diesem verbundenen Kolbenstange 92 führt auch zu einer Betätigung des Schaltelementes 104. Dadurch kann der Antrieb der Pumpe 10 abgeschaltet werden. Ein unnötiger Betrieb des Antriebes bei verschlossenem Düsenkopf wird dadurch vermieden.The movement of the control piston 78 and the associated piston rod 92 also leads to an actuation of the switching element 104. As a result, the drive of the pump 10 can be switched off. An unnecessary operation of the drive with a closed nozzle head is thereby avoided.

Die Wiederinbetriebnahme des Antriebes erfolgt, wenn der Düsenkopf geöffnet wird, denn dadurch kann über den Düsenkopf Reinigungsflüssigkeit abgegeben werden, so dass sich in der Druckleitung 50 eine Flüssigkeitsströmung ausbildet. Dies wiederum führt am Injektor 56 und damit auch in der Niederdruckkammer 80 zu einer Druckabsenkung und folglich zu einer Bewegung des Steuerkolbens 78 in Richtung des Verschlussstopfens 64. Der Steuerkolben 78 wird dann unter der Wirkung der Druckverhältnisse und unter der Wirkung der Druckfeder 116 wieder so weit in die dem Verschlussstopfen zugewandte Richtung verschoben, dass der Ventilkörper 90 seine Schließstellung einnimmt, in der er am Ventilsitz 88 anliegt. Außerdem wird durch die Verschiebung des Steuerkolbens 78 auch die Kolbenstange 92 und mit ihr der Schaltstößel 96 verschoben, so dass mittels des Schaltelements 104 der Antrieb der Pumpe 10 wieder eingeschaltet wird.The re-commissioning of the drive takes place when the nozzle head is opened, because it can be discharged through the nozzle head cleaning liquid, so that forms a liquid flow in the pressure line 50. This in turn leads to the injector 56 and thus also in the low pressure chamber 80 to a pressure drop and consequently to a movement of the control piston 78 in the direction of the closure plug 64. The control piston 78 is then under the effect of pressure conditions and under the action of the compression spring 116 again so far shifted in the direction of the closure plug facing that the valve body 90 assumes its closed position in which it rests against the valve seat 88. In addition, the displacement of the control piston 78, the piston rod 92 and moved with it the switching plunger 96, so that by means of the switching element 104, the drive of the pump 10 is turned on again.

Die Ausgestaltung des Ausgangsabschnittes 30 der Saugleitung in Form des Ringkanals 28, der in die rückseitige Trennfläche 20 des vorderen Gehäuseteils 16 eingeformt ist, hat den Vorteil, dass die Reinigungsflüssigkeit im Ausgangsabschnitt 30 nur sehr geringe Druckverluste erleidet. Die Zuführung von Reinigungsflüssigkeit zu den Pumpkammern 34 kann somit mit geringen Strömungsverlusten erfolgen.The configuration of the output section 30 of the suction line in the form of the annular channel 28, which is formed in the rear-side parting surface 20 of the front housing part 16, has the advantage that the cleaning liquid in the output section 30 suffers only very small pressure losses. The supply of cleaning fluid to the pumping chambers 34 can thus be carried out with low flow losses.

Darüber hinaus kann durch die ringförmige Ausgestaltung des Ausgangsabschnitts 30 der die Steuerkammer 66 ausbildende Durchgangskanal 62 praktisch an beliebiger Stelle an der Außenseite der Druckleitung 50 positioniert werden, wobei der Durchgangskanal 62 jeweils parallel zur Druckleitung 50 ausgerichtet ist. Dies gibt dem Konstrukteur verbesserte gestalterische Möglichkeiten und die Herstellungskosten der Pumpe 10 können gering gehalten werden.In addition, through the annular configuration of the output section 30 of the control chamber 66 forming passageway 62 is positioned virtually anywhere on the outside of the pressure line 50 be aligned with the passageway 62 each parallel to the pressure line 50. This gives the designer improved design options and the manufacturing cost of the pump 10 can be kept low.

Außerdem kann die Fertigung des Ausgangsabschnittes 30 verhältnismäßig einfach auf der Außenseite des vorderen Gehäuseteils 14 erfolgen, nämlich im Bereich der rückseitigen Trennfläche 20. Dies ermöglicht eine weitere Reduktion der Herstellungskosten der Pumpe 10.In addition, the production of the output section 30 can be relatively easily done on the outside of the front housing part 14, namely in the region of the rear parting surface 20. This allows a further reduction of the manufacturing cost of the pump 10th

Ein weiterer Vorteil des ringförmigen Ausgangsabschnittes 30 liegt darin, dass das untere Teilstück 110 der Bypassleitung sehr kurz gehalten werden kann. Dadurch kann der Druckverlust, den die Reinigungsflüssigkeit in der Bypassleitung erleidet, gering gehalten werden. Dies wiederum hat zur Folge, dass der in der Hochdruckkammer 82 herrschende Druck bei fehlender Durchströmung der Druckleitung 50 innerhalb sehr kurzer Zeit abgebaut werden kann und das Überströmventil 72 zuverlässig in seine Offenstellung übergeht.Another advantage of the annular output section 30 is that the lower portion 110 of the bypass line can be kept very short. As a result, the pressure loss that suffers the cleaning fluid in the bypass line can be kept low. This in turn has the consequence that the pressure prevailing in the high pressure chamber 82 pressure can be reduced within a very short time in the absence of flow through the pressure line 50 and the overflow valve 72 reliably passes into its open position.

Claims (15)

  1. Pump for a high-pressure cleaning appliance for delivering a cleaning liquid, comprising a pump housing (12) in which is arranged at least one pump chamber (34) into which at least one piston (36a, 36b) which is movable back and forth plunges, and which is connected via at least one inlet valve (44) to a suction line and via at least one outlet valve (48) to a pressure line (50), and comprising a bypass line (70, 110) which leads from the pressure line (50) to the suction line, and in which is arranged an overflow valve (72), the valve body (90) of which is connected to a control element which in dependence upon the flow rate of the cleaning liquid in the pressure line (50) displaces the valve body (90) to a closed position or an open position, characterized in that the pump housing (12) comprises a rear housing component (14) and a front housing component (16) which are joined together, and in that the suction line comprises a suction line section (30) which extends in the joining area between the two housing components (14, 16), and into which the bypass line (70, 110) opens.
  2. Pump in accordance with claim 1, characterized in that the suction line section (30) is arcuately curved at least in a portion thereof.
  3. Pump in accordance with claim 1 or 2, characterized in that the suction line section (30) is configured as a self-contained ring.
  4. Pump in accordance with claim 1, 2 or 3, characterized in that the suction line section forms an outlet section (30) of the suction line.
  5. Pump in accordance with any one of the preceding claims, characterized in that the suction line comprises an inlet section (32) arranged in the front housing component (16), and in that the suction line section arranged in the joining area between the two housing components (14, 16) forms an outlet section (30) of the suction line.
  6. Pump in accordance with any one of the preceding claims, characterized in that the front housing component (16) comprises a rear-side separating surface (20) which is placed on a front-side separating surface (22) of the rear housing component (14) with at least one sealing element (24, 26) interposed between these, a channel (28) constituting at least a portion of the suction line section (30) being formed in at least one of the separating surfaces (20, 22).
  7. Pump in accordance with claim 6, characterized in that there is formed in the rear-side separating surface (20) of the front housing component (16) a channel (28) which is covered by the front-side separating surface (22) of the rear housing component (14) and constitutes the suction line section (30).
  8. Pump in accordance with any one of the preceding claims, characterized in that the suction line section (30) surrounds at least partly the pressure line (50) at a distance therefrom.
  9. Pump in accordance with any one of the preceding claims, characterized in that the control element is configured as a control piston (78) which divides a control chamber (66) of the front housing component (16) into a low-pressure chamber (80) and a high-pressure chamber (82), is displaceable in the control chamber (66) and is connected by a piston rod (92) to the valve body (90) of the overflow valve (72), the low-pressure chamber (80) being connected by a control line (108) downstream of a throttle point to the pressure line (50), and the high-pressure chamber (82) being connected to the pressure line by a portion (110) of the bypass line that is arranged upstream of the overflow valve (72).
  10. Pump in accordance with claim 9, characterized in that the piston rod (92) forms on the side of the valve body (90) that faces away from the control piston (78) a plunger (96) for actuating a switch element (104).
  11. Pump in accordance with claim 9 or 10, characterized in that the valve body (90) is configured as a radial widening of the piston rod (92).
  12. Pump in accordance with claim 10, characterized in that the plunger (96) sinks into a receptacle (102) which is formed in the rear housing component (14), and in which the switch element (104) is arranged.
  13. Pump in accordance with any one of claims 9 to 12, characterized in that the bypass line comprises a portion (70) which accommodates the overflow valve, opens into the suction line section (30) arranged in the joining area between the two housing components (14, 16) and is oriented in alignment with the control chamber (66).
  14. Pump in accordance with claim 13, characterized in that the control chamber (66) and the portion (70) of the bypass line that accommodates the overflow valve (72) are oriented parallel to the pressure line (50).
  15. Pump in accordance with claim 13 or 14, characterized in that the control chamber (66) and the portion (70) of the bypass line that accommodates the overflow valve (72) are arranged in a through-channel (62) which passes through the front housing component (16) from a front side (52) to a rear-side separating surface (20).
EP10765399.0A 2009-10-01 2010-09-24 Pump for a high-pressure cleaning device Active EP2483560B1 (en)

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DE102009049094A DE102009049094A1 (en) 2009-10-01 2009-10-01 Pump for a high-pressure cleaning device
PCT/EP2010/064162 WO2011039117A1 (en) 2009-10-01 2010-09-24 Pump for a high-pressure cleaning device

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EP (1) EP2483560B1 (en)
CN (1) CN102686882B (en)
BR (1) BR112012007599A2 (en)
DE (1) DE102009049094A1 (en)
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PL2805055T3 (en) * 2012-01-20 2016-11-30 Piston pump for a high-pressure cleaning device
DE102014106673A1 (en) * 2014-05-12 2015-11-12 Alfred Kärcher Gmbh & Co. Kg High pressure pump for ultrahigh pressure applications
WO2016097853A1 (en) 2014-12-19 2016-06-23 Daniele Marino Liquid discharge device
EP4079419A1 (en) 2014-12-23 2022-10-26 Alfred Kärcher SE & Co. KG High-pressure cleaning device
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BR112012007599A2 (en) 2020-10-20
US8684699B2 (en) 2014-04-01
EP2483560A1 (en) 2012-08-08
CN102686882B (en) 2015-03-25
US20120211034A1 (en) 2012-08-23
DK2483560T3 (en) 2015-03-23
DE102009049094A1 (en) 2011-04-07
ES2534278T3 (en) 2015-04-21
CN102686882A (en) 2012-09-19
PL2483560T3 (en) 2015-07-31
WO2011039117A1 (en) 2011-04-07

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