EP0608796B1 - Pressure and suction distributor for high pressure cleaning apparatus with an additional control valve - Google Patents

Pressure and suction distributor for high pressure cleaning apparatus with an additional control valve Download PDF

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Publication number
EP0608796B1
EP0608796B1 EP94100936A EP94100936A EP0608796B1 EP 0608796 B1 EP0608796 B1 EP 0608796B1 EP 94100936 A EP94100936 A EP 94100936A EP 94100936 A EP94100936 A EP 94100936A EP 0608796 B1 EP0608796 B1 EP 0608796B1
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EP
European Patent Office
Prior art keywords
pressure
valve
high pressure
bypass valve
spring
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.)
Expired - Lifetime
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EP94100936A
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German (de)
French (fr)
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EP0608796A1 (en
Inventor
Rainer Oberdorfer-Bögel
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WAP Reinigungssysteme GmbH and Co
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WAP Reinigungssysteme GmbH and Co
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Publication of EP0608796A1 publication Critical patent/EP0608796A1/en
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    • BPERFORMING OPERATIONS; TRANSPORTING
    • B05SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05BSPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B9/00Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour
    • B05B9/03Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour characterised by means for supplying liquid or other fluent material
    • B05B9/04Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour characterised by means for supplying liquid or other fluent material with pressurised or compressible container; with pump
    • B05B9/0403Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour characterised by means for supplying liquid or other fluent material with pressurised or compressible container; with pump with pumps for liquids or other fluent material
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B08CLEANING
    • B08BCLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B3/00Cleaning by methods involving the use or presence of liquid or steam
    • B08B3/02Cleaning by the force of jets or sprays
    • B08B3/026Cleaning by making use of hand-held spray guns; Fluid preparations therefor
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B08CLEANING
    • B08BCLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B2203/00Details of cleaning machines or methods involving the use or presence of liquid or steam
    • B08B2203/02Details of machines or methods for cleaning by the force of jets or sprays
    • B08B2203/0205Bypass pressure relief valves

Definitions

  • the present invention relates to a pressure-suction distributor according to the preamble of patent claim 1.
  • Such pressure-suction distributors are used at the outlet of high-pressure pumps in order to supply the high-pressure water to a downstream control valve.
  • This control valve has the task of briefly opening the engine during the start-up phase and allowing an overflow to the low-pressure side in order to facilitate the start-up of the drive motor for the high-pressure cleaner.
  • a control valve is known which has been found in several applications by the same applicant.
  • Such an embodiment offers the advantage that if there is an undervoltage, which can be caused by corresponding fluctuations in the tolerance of the mains voltage or by an appropriately undersized extension cable with a corresponding length, the machine still starts up.
  • the drive motor of the high-pressure cleaner then starts up only with difficulty. Such difficult conditions arise especially when high pressure is present on the high-pressure side in the area of the shut-off gun, going back to the pressure chamber of the pump. It can happen that starting the drive motor is made difficult under extreme conditions.
  • the BYPASS control arrangement for high-pressure washing systems which is to be regarded as the closest prior art and is described in US Pat. No. 5,035,580, has a throttle valve connected to a separate high-pressure connection of a pump, which is open in the pump idle state and thus a way between the high pressure connection and the low pressure connection of the pump and only closes when the spray gun is open, i.e. at maximum water pressure.
  • the invention is therefore based on the object of providing a pressure-suction distributor for a high-pressure cleaning device with a special advantageous bypass valve arrangement / design in order to ensure that the drive motor of the device is started even when working with extreme undervoltage and when High pressure is present on the high pressure side and is not released by the switch-off gun.
  • the invention is characterized by the technical teaching of claim 1.
  • the spring-loaded bypass valve is arranged in the flow direction upstream of the control valve along the high-pressure line running to the spray nozzle and connects it to the low-pressure line.
  • the bypass valve is pressure-controlled in such a way that it opens a flow path between the high-pressure line and the low-pressure line when the pressure rises and closes this flow path again when a certain increased pressure is reached.
  • This bypass valve is held in the closed position with a spring in such a way that in the event of a pressure surge which is below the working pressure, the valve gets into an unstable state, ie between the open and the closed position and here from the high-pressure side to the low-pressure side, a water flow for a short time the valve flows through. Before the working pressure is reached, the valve closes again, so that the normal function of the control valve is established at least when the working pressure is reached.
  • bypass valve is arranged at the outlet of the high-pressure pump in front of the control valve, because an arrangement after the control valve would not make sense because there are other valves which could impair the function of the bypass valve according to the invention.
  • the bypass line and the bypass valve are integrated in the control valve.
  • the pressure equalization takes place here via a valve arranged at the front end of the control slide, which, depending on the prevailing pressure conditions, assumes a position between two valve seats. Depending on the position of the valve ball from the high-pressure line, the pressure equalization takes place past the control slide through the rear end of the valve sleeve into the low pressure lines.
  • the control valve 1 is a known part and consists essentially of a spring 18 which is supported at one end on the housing of the control valve 1 and which bears at its other end on a control slide 27 which is guided in a sleeve 17 .
  • the control valve 1 is shown in half section in the open and closed position.
  • the control slide 27 acts on a valve ball 16 which cooperates with a valve seat 15.
  • a valve seat 15 Via the high-pressure inlet 2 from the outlet of the pump on the pump side 3 High-pressure medium fed into the channel 8, which is connected directly to the high-pressure inlet 2.
  • the bypass valve 9, 10, 11, 12, 13 is arranged in the region of the channel 8. It essentially consists of an upper valve seat 11 and a lower valve seat 12 arranged in a sleeve 9. Between the upper and lower valve seats 11, 12, the valve ball 10 is arranged spring-loaded by the spring 13. In the closed position shown, the valve ball 10 rests spring-loaded on the upper valve seat 11.
  • valve ball 10 between the two valve seats 11, 12 is in an unstable state and water therefore flows from the high-pressure inlet via the channel 8 into the channel 14, which is connected directly to the low-pressure ring channel 6 , via which the water flows back in the direction of arrow 19 to the pump side 3.
  • the high-pressure water flows through the high-pressure inlet 2 in the direction of the arrow 20 to the control valve 1, which is open as intended, after which the water is then fed via the high-pressure outlet 7 to further pressure valves and then to the manual shut-off gun and finally to the spray nozzle.
  • the bypass valve according to the invention is part of a pressure-suction distributor 4 which is flanged directly to the pump side 3 of the high-pressure pump and acts as a cover.
  • the pressure-suction distributor is closed on its high-pressure side with a stopper 5.
  • the drive motor of the pump is started at position 21 and the operating pressure increases until it has reached approximately position 22.
  • the valve ball 10 is lifted from its seat 10 against the force of the spring 13 and water flows briefly over it Bypass valve in the channel 14 and thus back to the low pressure side of the ring channel 6. This relieves the high pressure side of the pump and makes it easier for the drive motor to crank.
  • the pressure increase due to this water drainage, takes place with a smaller gradient when the bypass valve 9, 10, 11, 12, 13 is open, that is to say in the area between positions 22 and 23.
  • bypass valve 9, 10, 11, 12, 13 shown With the bypass valve 9, 10, 11, 12, 13 shown, a bypass flow from the high-pressure outlet side of the pump to the low-pressure side of the pump is briefly generated in order to briefly prevent the pump from starting up against high pressure at the outlet, in order to start the engine of the drive motor to guarantee.
  • bypass valve according to the invention is double-acting. If the HD pump sucks its water out of a container via a suction hose, then it is prevented that the in the Air 8 located in the bypass valve which is already closed (the closing process is effected automatically via spring 13) is not pressed into the ring channel 6.
  • both the bypass line and the bypass valve 16, 30, 31, 36 are also integrated in the control valve 1.
  • the bypass line is formed by a valve sleeve 28 which coaxially surrounds the control slide 27 and whose inside diameter is larger than the outside diameter of the control slide 27.
  • the inner sleeve diameter is selected such that a spring 30 is located between the inner sleeve wall and the control slide 27, which is inserted over the control slide 27 and against its shoulder 34 supports.
  • the other end of the spring 30 exerts a spring force on the valve ball 16 and presses it in a direction away from the end face 32 of the control slide 27 against a valve seat 31 which is formed at the front end of the valve sleeve 28.
  • This valve seat 31 is preferably designed as a plastic ring and represents the inlet opening of the bypass line.
  • the outlet opening 29 of the bypass line is formed by radial bores at the rear end of the valve sleeve 28, these radial bores of the outlet opening 29 Connect the bypass line to the low pressure lines.
  • valve ball 16 In the closed position, the valve ball 16 is pressed by the spring 30 against the valve seat 31. In this position, the valve ball 16 is at a certain distance from the end face 32 of the control slide 27, which is predetermined on the one hand by the dimensions of the valve sleeve 28 with the valve seat 31 and on the other hand by the length of the control slide 27.
  • valve ball 16 When pressure builds up on the pressure side, the valve ball 16 is displaced from its valve seat 31 against the force of the spring 30 in the direction of arrow 35 toward the end face 32 of the control slide 27, and the bypass valve 16, 30, 31, 36 is thus opened. A pressure equalization can now take place from the high pressure side through the bypass line via the outlet opening 29 of the valve sleeve 28 into the suction lines or low pressure lines. With increasing pressure build-up on the pressure side, the valve ball 16 is finally pressed against the end face 32 of the control slide 27. At the same time, however, the control slide 27 also backs up against the bias of the spring 30 until finally, after the set maximum pressure has been reached, the valve ball 16 comes to rest in the valve seat 36 and the bypass valve closes.
  • the lower limit pressure at which the bypass valve 16, 30, 31, 36 is to be opened or at which lower value the desired pressure equalization in the high-pressure line is to be set can thus be set via the spring 30.
  • the pressure range in which the bypass valve 16, 30, 31, 36 is to be opened is adjustable by the force of the spring 30, so that a conductive connection is established between the pressure side and the low pressure side.
  • a second parameter determining the pressure range is the distance between the two valve seats 31 and 36, which determines the possible displacement path of the valve ball 16.
  • the working pressure which is to prevail on the pressure side after the high-pressure pump has started up can also be adjusted in this embodiment by the spring 18 of the control valve 1.
  • the force of the spring 18 can in fact be used to set the value of the required pressure which is necessary in order to be able to push the control slide 27 upward in the direction of arrow 35, so that finally the valve ball 16 rests on the valve seat 36 and the bypass valve 16, 30, 31 , 36 closes after the working pressure is reached.

Abstract

The present invention relates to a pressure and suction distributor for a high-pressure cleaning apparatus with low-pressure lines, in which water is fed to the high-pressure pump, and high-pressure lines, which run from the high-pressure pump to a spray nozzle, and with a control valve which is provided along the high-pressure lines to allow these to be shut off or opened selectively. In order to delay a pressure build-up in the high-pressure lines (2, 8) during the start-up process of the pump motor, the high-pressure lines (2, 8) in the pressure and suction distributor according to the invention are connected via a bypass line (14) that can be closed in a pressure-controlled manner to the low-pressure lines (6). Provided along this bypass line (14) is a bypass valve (9, 10, 11, 12, 13) which, as a function of the pressure, opens or closes a flow path (14) between the high-pressure lines (2, 8) and the low-pressure lines (6). <IMAGE>

Description

Gegenstand der vorliegenden Erfindung ist ein Druck-Saugverteiler nach dem Oberbegriff des Patentanspruchs 1. Derartige Druck-Saugverteiler werden am Auslaß von Hochdruckpumpen verwendet, um das Hochdruckwasser einem nachgeschalteten Steuerventil zuzuführen. Dieses Steuerventil hat die Aufgabe, in der Anlaufphase den Motor kurzzeitig zu öffnen und eine Überströmung zur Niederdruckseite zu ermöglichen, um den Anlauf des Antriebsmotors für den Hochdruckreiniger zu erleichtern.The present invention relates to a pressure-suction distributor according to the preamble of patent claim 1. Such pressure-suction distributors are used at the outlet of high-pressure pumps in order to supply the high-pressure water to a downstream control valve. This control valve has the task of briefly opening the engine during the start-up phase and allowing an overflow to the low-pressure side in order to facilitate the start-up of the drive motor for the high-pressure cleaner.

Es ist hierbei ein Steuerventil bekannt, welches in mehreren Anmeldungen des gleichen Anmelders Niederschlag gefunden hat.A control valve is known which has been found in several applications by the same applicant.

Eine solche Ausführungsform bietet den Vorteil, daß bei Vorliegen einer Unterspannung, die hervorgerufen werden kann durch entsprechende Toleranzschwankungen der Netzspannung oder durch ein entsprechend unterdimensioniertes Verlängerungskabel mit entsprechender Länge, die Maschine trotzdem anläuft.Such an embodiment offers the advantage that if there is an undervoltage, which can be caused by corresponding fluctuations in the tolerance of the mains voltage or by an appropriately undersized extension cable with a corresponding length, the machine still starts up.

Der Antriebsmotor des Hochdruckreinigers läuft dann allerdings nur erschwert an. Derartig erschwerte Bedingungen entstehen vor allem dann, wenn auf der Hochdruckseite im Bereich der Abschaltpistole zurückgehend bis in den Druckraum der Pumpe, Hochdruck ansteht. Hierbei kann es passieren, daß bei extremen Verhältnissen ein Anlauf des Antriebsmotors erschwert wird.The drive motor of the high-pressure cleaner then starts up only with difficulty. Such difficult conditions arise especially when high pressure is present on the high-pressure side in the area of the shut-off gun, going back to the pressure chamber of the pump. It can happen that starting the drive motor is made difficult under extreme conditions.

Die als nächstliegender Stand der Technik anzusehende, in der US-A-5,035,580 beschriebene BYPASS-Kontroll-Anordnung für Hochdruck-Waschsysteme, weist ein, an einem separaten Hochdruckanschluß einer Pumpe angegeschlossenes Drosselventil auf, welches im Pumpen-Ruhezustand geöffnet ist und somit einen Weg zwischen Hochdruckanschluß und Niederdruckanschluß der Pumpe freigibt und erst bei geöffneter Sprühpistole, also bei maximalem Wasserdruck, schließt.The BYPASS control arrangement for high-pressure washing systems, which is to be regarded as the closest prior art and is described in US Pat. No. 5,035,580, has a throttle valve connected to a separate high-pressure connection of a pump, which is open in the pump idle state and thus a way between the high pressure connection and the low pressure connection of the pump and only closes when the spray gun is open, i.e. at maximum water pressure.

Der Erfindung liegt deshalb die Aufgabe zugrunde, einen Druck-Saugverteiler für ein Hochdruckreinigungsgerät mit spezieller vorteilhafter Bypassventil-Anordnung/-Ausbildung zur Verfügung zu stellen, um das Anlaufen des Antriebsmotors des Gerätes auch dann zu gewährleisten, wenn mit extremer Unterspannung gearbeitet wird und wenn ein Hochdruck auf der Hochdruckseite ansteht und durch die Abschaltpistole nicht abgelassen wird.The invention is therefore based on the object of providing a pressure-suction distributor for a high-pressure cleaning device with a special advantageous bypass valve arrangement / design in order to ensure that the drive motor of the device is started even when working with extreme undervoltage and when High pressure is present on the high pressure side and is not released by the switch-off gun.

Im übrigen gibt es auch noch Betriebszustände beim Betrieb derartiger Hochdruckreinigungsmaschinen, wobei bei Niederdruck seitens der Abschaltpistole, ein Anlauf gegen das federbelastete Ventil des Steuerventils notwendig ist. Auch für diesen Fall soll der Wiederanlauf des Antriebsmotors des Hochdruckreinigers sichergestellt werden.In addition, there are also operating states during the operation of such high-pressure cleaning machines, a start against the spring-loaded valve of the control valve being necessary at low pressure on the part of the shut-off gun. In this case too, the restart of the high-pressure cleaner drive motor should be ensured.

Zur Lösung der gestellten Aufgabe ist die Erfindung durch die technische Lehre des Anspruchs 1 gekennzeichnet.To achieve the object, the invention is characterized by the technical teaching of claim 1.

Wesentliches Merkmal der Erfindung ist, daß das federbelastete Bypassventil in Strömungsrichtung vor dem Steuerventil entlang der zur Sprühdüse verlaufenden Hochdruckleitung angeordnet ist und diese mit der Niederdruckleitung verbindet. Dabei ist das Bypassventil derart druckgesteuert, daß es beim Ansteigen des Druckes einen Strömungsweg zwischen der Hochdruckleitung und der Niederdruckleitung öffnet und diesen Strömungsweg bei Erreichen eines bestimmten erhöhten Druckes wieder schließt. Dieses Bypassventil wird mit einer Feder derart in Schließstellung gehalten, daß bei einem Druckstoß, der unterhalb des Arbeitsdruckes liegt, das Ventil in einen instabilen Zustand gerät, d. h. zwischen der Öffnungs- und der Schließstellung und hierbei von der Hochdruckseite zur Niederdruckseite, kurzzeitig ein Wasserstrom durch das Ventil hindurchströmt. Vor Erreichen des Arbeitsdruckes schließt das Ventil bereits schon wieder, so daß mindestens mit Erreichen des Arbeitsdruckes die normale Funktion des Steuerventils hergestellt wird.An essential feature of the invention is that the spring-loaded bypass valve is arranged in the flow direction upstream of the control valve along the high-pressure line running to the spray nozzle and connects it to the low-pressure line. The bypass valve is pressure-controlled in such a way that it opens a flow path between the high-pressure line and the low-pressure line when the pressure rises and closes this flow path again when a certain increased pressure is reached. This bypass valve is held in the closed position with a spring in such a way that in the event of a pressure surge which is below the working pressure, the valve gets into an unstable state, ie between the open and the closed position and here from the high-pressure side to the low-pressure side, a water flow for a short time the valve flows through. Before the working pressure is reached, the valve closes again, so that the normal function of the control valve is established at least when the working pressure is reached.

D. h., nur kurzzeitig beim Anlauf der Reinigungsmaschine wird über die besagte Bypassöffnung und das darin angeordnete, federbelastete Ventil ein Bypasstrom von der Hochdruckseite zur Niederdruckseite geleitet, wodurch die Hochdruckseite der Pumpe entlastet wird, weil der entsprechende Gegendruck auf den Pumpenkolben fehlt und hierdurch der Antriebsmotor einen erleichterten Anlauf hat.This means that a bypass flow is directed from the high-pressure side to the low-pressure side only briefly when the cleaning machine starts up via the bypass opening and the spring-loaded valve arranged therein, whereby the high-pressure side of the pump is relieved because the corresponding counterpressure on the pump piston is absent and thereby the drive motor has an easier start.

Wesentlich hierbei ist, daß das besagte Bypassventil am Ausgang der Hochdruckpumpe vor dem Steuerventil angeordnet ist, weil eine Anordnung nach dem Steuerventil nicht sinnvoll wäre, weil dort weitere Ventile vorhanden sind, welche die Funktion des erfindungsgemäßen Bypassventils beeinträchtigen könnten.It is essential here that said bypass valve is arranged at the outlet of the high-pressure pump in front of the control valve, because an arrangement after the control valve would not make sense because there are other valves which could impair the function of the bypass valve according to the invention.

Bei einer bevorzugten Ausführungsform der vorliegenden Erfindung sind die Bypassleitung und das Bypassventil in dem Steuerventil integriert. Der Druckausgleich erfolgt hierbei über ein am vorderen Ende des Steuerschiebers angeordnetes Ventil, welches je nach den vorherrschenden Druckverhältnissen, eine Position zwischen zwei Ventilsitzen einnimmt. Dabei findet der Druckausgleich, je nach Position der Ventilkugel von der Hochdruckleitung, vorbei an dem Steuerschieber durch das hintere Ende der Ventilhülse in die Niederdruckleitungen statt.In a preferred embodiment of the present invention, the bypass line and the bypass valve are integrated in the control valve. The pressure equalization takes place here via a valve arranged at the front end of the control slide, which, depending on the prevailing pressure conditions, assumes a position between two valve seats. Depending on the position of the valve ball from the high-pressure line, the pressure equalization takes place past the control slide through the rear end of the valve sleeve into the low pressure lines.

Bei diesem Ausführungsbeispiel ist kein separates Druckentlastungsventil erforderlich, sondern die Druckentlastung kann ohne wesentlichen Kostenaufwand lediglich durch eine entsprechende Umgestaltung des Steuerventils erreicht werden.In this embodiment, a separate pressure relief valve is not required, but the pressure relief can be achieved without substantial cost simply by appropriately redesigning the control valve.

Im folgenden wird die Erfindung anhand von mehrere Ausführungswege darstellenden Zeichnungen näher erläutert. Hierbei gehen aus den Zeichnungen und ihrer Beschreibung weitere wesentliche Merkmale und Vorteile der Erfindung hervor.In the following, the invention will be explained in more detail with reference to drawings showing several possible embodiments. Further essential features and advantages of the invention emerge from the drawings and their description.

Es zeigen:

Figur 1:
Schnitt durch ein Steuerventil und einen Druck-Saugverteiler mit dem erfindungsgemäßen Bypassventil;
Figur 2:
ein Druck-Zeitdiagramm eines Hochdruckreinigungsgerätes.
Figur 3:
einen Schnitt durch ein Steuerventil mit einem integrierten erfindungsgemäßen Bypassventil.
Show it:
Figure 1:
Section through a control valve and a pressure-suction manifold with the bypass valve according to the invention;
Figure 2:
a pressure-time diagram of a high-pressure cleaning device.
Figure 3:
a section through a control valve with an integrated bypass valve according to the invention.

Das Steuerventil 1 ist ein an sich bekanntes Teil und besteht im wesentlichen aus einer Feder 18, die sich mit ihrem einen Ende am Gehäuse des Steuerventils 1 abstützt und die mit ihrem anderen Ende an einem Steuerschieber 27 anliegt, der in einer Büchse 17 verschiebbar geführt ist. Das Steuerventil 1 ist jeweils im Halbschnitt in geöffneter und geschlossener Position gezeigt.The control valve 1 is a known part and consists essentially of a spring 18 which is supported at one end on the housing of the control valve 1 and which bears at its other end on a control slide 27 which is guided in a sleeve 17 . The control valve 1 is shown in half section in the open and closed position.

Der Steuerschieber 27 wirkt auf eine Ventilkugel 16, die mit einem Ventilsitz 15 zusammenwirkt. Über den Hochdruck-Einlaß 2 wird vom Auslaß der Pumpe auf der Pumpenseite 3 ein Hochdruckmedium in den Kanal 8 eingespeist, der direkt mit dem Hochdruck-Einlaß 2 verbunden ist. Im Bereich des Kanals 8 ist das erfindungsgemäße Bypassventil 9,10,11,12,13 angeordnet. Es besteht im wesentlichen aus einem, in einer Büchse 9 angeordneten, oberen Ventilsitz 11 und einem unteren Ventilsitz 12. Zwischen dem oberen und unteren Ventilsitz 11, 12 ist die Ventilkugel 10 federbelastet durch die Feder 13 angeordnet. In der gezeigten Schließstellung liegt die Ventilkugel 10 federbelastet am oberen Ventilsitz 11 an.The control slide 27 acts on a valve ball 16 which cooperates with a valve seat 15. Via the high-pressure inlet 2 from the outlet of the pump on the pump side 3 High-pressure medium fed into the channel 8, which is connected directly to the high-pressure inlet 2. The bypass valve 9, 10, 11, 12, 13 is arranged in the region of the channel 8. It essentially consists of an upper valve seat 11 and a lower valve seat 12 arranged in a sleeve 9. Between the upper and lower valve seats 11, 12, the valve ball 10 is arranged spring-loaded by the spring 13. In the closed position shown, the valve ball 10 rests spring-loaded on the upper valve seat 11.

Bei Überwindung des Druckes der Feder 13 befindet sich die Ventilkugel 10 zwischen den beiden Ventilsitzen 11, 12 in einem instabilen Zustand und es fließt somit Wasser von dem Hochdruckeinlaß über den Kanal 8 in den Kanal 14, der direkt mit dem Niederdruck-Ringkanal 6 verbunden ist, über welchen das Wasser in Pfeilrichtung 19 zur Pumpenseite 3 zurückfließt.When the pressure of the spring 13 is overcome, the valve ball 10 between the two valve seats 11, 12 is in an unstable state and water therefore flows from the high-pressure inlet via the channel 8 into the channel 14, which is connected directly to the low-pressure ring channel 6 , via which the water flows back in the direction of arrow 19 to the pump side 3.

Im normalen Betriebszustand fließt das Hochdruckwasser über den Hochdruck-Einlaß 2 in Pfeilrichtung 20 zu dem Steuerventil 1, welches bestimmungsgemäß geöffnet ist, wonach dann das Wasser über den Hochdruckauslaß 7 weiteren Druckventilen und dann der Handabschaltpistole und schließlich dann der Sprühdüse zugeführt wird.In the normal operating state, the high-pressure water flows through the high-pressure inlet 2 in the direction of the arrow 20 to the control valve 1, which is open as intended, after which the water is then fed via the high-pressure outlet 7 to further pressure valves and then to the manual shut-off gun and finally to the spray nozzle.

Das erfindungsgemäße Bypassventil ist Teil eines Druck-Saugverteilers 4, der direkt an der Pumpenseite 3 der Hochdruckpumpe angeflanscht ist und als Deckel wirkt. Der Druck-Saugverteiler ist an seiner Hochdruckseite mit einem Stopfen 5 verschlossen.The bypass valve according to the invention is part of a pressure-suction distributor 4 which is flanged directly to the pump side 3 of the high-pressure pump and acts as a cover. The pressure-suction distributor is closed on its high-pressure side with a stopper 5.

Gemäß Figur 2 wird bei Position 21 der Antriebsmotor der Pumpe gestartet und der Betriebsdruck steigt an, bis er etwa Position 22 erreicht hat. In dieser Position wird die Ventilkugel 10 entgegen der Kraft der Feder 13 von ihrem Sitz 10 abgehoben und es fließt kurzzeitig Wasser über das Bypassventil in den Kanal 14 und somit zur Niederdruckseite des Ringkanals 6 zurück. Damit wird die Hochdruckseite der Pumpe entlastet und der Antriebsmotor kann leichter durchdrehen. Gleichzeitig erfolgt jedoch der Druckanstieg, bedingt durch diese Wasserableitung, bei geöffnetem Bypassventil 9, 10,11,12,13, also im Bereich zwischen den Positionen 22 und 23, mit einer geringeren Steigung.According to FIG. 2, the drive motor of the pump is started at position 21 and the operating pressure increases until it has reached approximately position 22. In this position, the valve ball 10 is lifted from its seat 10 against the force of the spring 13 and water flows briefly over it Bypass valve in the channel 14 and thus back to the low pressure side of the ring channel 6. This relieves the high pressure side of the pump and makes it easier for the drive motor to crank. At the same time, however, the pressure increase, due to this water drainage, takes place with a smaller gradient when the bypass valve 9, 10, 11, 12, 13 is open, that is to say in the area between positions 22 and 23.

Sobald der Betriebsdruck bei Position 23 angestiegen ist, liegt die Ventilkugel 10 an dem gegenüberliegenden Ventilsitz 12 an und somit ist das Bypassventil 9,10,11,12,13 wieder geschlossen. Nachdem in diesem Zustand der Antriebsmotor bereits schon auf vollen Touren läuft, spielt es keine Rolle mehr, wenn die Hochdruckpumpe an ihrem Auslaß gegen einen entsprechenden Gegendruck arbeiten muß. Der Betriebsdruck steigt dann insbesondere bei geschlossener Spritzpistole weiter an und überschreitet in der Regel den Arbeitsdruck bei Position 24 um einen bestimmten überschießenden Druck bei Position 25, den Abschaltdruck. Nach Erreichen dieses Abschaltdruckes bei Position 25, ist der Druckaufbau des Anlaufvorgangs abgeschlossen und der Betriebsdruck pegelt sich auf der Hochdruckseite der Pumpe bei Position 26 schließlich auf den Arbeitsdruck ein.As soon as the operating pressure has risen at position 23, the valve ball 10 rests on the opposite valve seat 12 and the bypass valve 9, 10, 11, 12, 13 is thus closed again. After the drive motor is already running at full speed in this state, it no longer matters if the high-pressure pump has to work at its outlet against a corresponding counter pressure. The operating pressure then increases further, particularly when the spray gun is closed, and generally exceeds the working pressure at position 24 by a certain excess pressure at position 25, the cut-off pressure. After reaching this switch-off pressure at position 25, the pressure build-up of the start-up process is complete and the operating pressure on the high-pressure side of the pump at position 26 is finally adjusted to the working pressure.

Mit dem dargestellten Bypassventil 9,10,11,12,13 wird also kurzzeitig ein Bypassfluß von der Hochdruck-Auslaßseite der Pumpe zur Niederdruckseite der Pumpe erzeugt, um ein Anlaufen der Pumpe gegen einen Hochdruck am Auslaß kurzzeitig zu vermeiden, um den Motoranlauf des Antriebsmotors zu gewährleisten.With the bypass valve 9, 10, 11, 12, 13 shown, a bypass flow from the high-pressure outlet side of the pump to the low-pressure side of the pump is briefly generated in order to briefly prevent the pump from starting up against high pressure at the outlet, in order to start the engine of the drive motor to guarantee.

Wichtig ist, daß das erfindungsgemäße Bypassventil doppelt wirkend ist. Saugt nämlich die HD-Pumpe ihr Wasser über einen Saugschlauch aus einem Behälter, dann wird verhindert, daß während des Beginns des Ansaugvorganges die in der Leitung 8 befindliche Luft über das bereits geschlossene Bypassventil (Schließvorgang wird automatisch über Feder 13 bewirkt) nicht in den Ringkanal 6 gedrückt wird.It is important that the bypass valve according to the invention is double-acting. If the HD pump sucks its water out of a container via a suction hose, then it is prevented that the in the Air 8 located in the bypass valve which is already closed (the closing process is effected automatically via spring 13) is not pressed into the ring channel 6.

Damit wird sichergestellt, daß die HD-Pumpe auch einwandfrei ansaugen kann und kein Luft- oder Wasserrückfluß von der Saugseite der HD-Pumpe zur Druckseite stattfinden kann. Auf diese Weise wird ein unzulässiges Umwälzen der Luft vermieden und eine einwandfreie Entlüftung der Pumpe sichergestellt.This ensures that the HP pump can also suck in properly and that no air or water can flow back from the suction side of the HP pump to the pressure side. In this way, an inadmissible circulation of the air is avoided and proper venting of the pump is ensured.

Bei der in Figur 3 dargestellten Ausführungsform sind sowohl die Bypassleitung als auch das Bypassventil 16,30,31,36 mit in das Steuerventil 1 integriert. Die Bypassleitung wird dabei von einer Ventilhülse 28 gebildet, welche koaxial den Steuerschieber 27 umgibt und deren Innendurchmesser größer als der Außendurchmesser des Steuerschiebers 27 ist. Bei der so als Zwischenraum zwischen dem Steuerschieber 27 und der Innenwandung der Ventilhülse 28 gebildeten Bypassleitung ist der Hülseninnendurchmesser derart gewählt, daß zwischen der Hülseninnenwandung und dem Steuerschieber 27 eine Feder 30 Platz findet, welche über den Steuerschieber 27 gesteckt ist und sich gegen dessen Schulter 34 abstützt.In the embodiment shown in FIG. 3, both the bypass line and the bypass valve 16, 30, 31, 36 are also integrated in the control valve 1. The bypass line is formed by a valve sleeve 28 which coaxially surrounds the control slide 27 and whose inside diameter is larger than the outside diameter of the control slide 27. In the bypass line thus formed as an intermediate space between the control slide 27 and the inner wall of the valve sleeve 28, the inner sleeve diameter is selected such that a spring 30 is located between the inner sleeve wall and the control slide 27, which is inserted over the control slide 27 and against its shoulder 34 supports.

Das andere Ende der Feder 30 übt eine Federkraft auf die Ventilkugel 16 aus und drückt diese in einer Richtung weg von der Stirnseite 32 des Steuerschiebers 27 gegen einen Ventilsitz 31, der am vorderen Ende der Ventilhülse 28 ausgebildet ist.The other end of the spring 30 exerts a spring force on the valve ball 16 and presses it in a direction away from the end face 32 of the control slide 27 against a valve seat 31 which is formed at the front end of the valve sleeve 28.

Dieser Ventilsitz 31 ist vorzugsweise als Kunststoffring ausgebildet und stellt die Eintrittsöffnung der Bypassleitung dar. Die Austrittsöffnung 29 der Bypassleitung wird von radialen Bohrungen am hinteren Ende der Ventilhülse 28 gebildet, wobei diese radialen Bohrungen der Austrittsöffnung 29 die Bypassleitung mit den Niederdruckleitungen verbinden.This valve seat 31 is preferably designed as a plastic ring and represents the inlet opening of the bypass line. The outlet opening 29 of the bypass line is formed by radial bores at the rear end of the valve sleeve 28, these radial bores of the outlet opening 29 Connect the bypass line to the low pressure lines.

In Schließstellung wird die Ventilkugel 16 von der Feder 30 gegen den Ventilsitz 31 gedrückt. In dieser Stellung befindet sich die Ventilkugel 16 in einem bestimmten Abstand zur Stirnseite 32 des Steuerschiebers 27, welcher einerseits durch die Abmessungen der Ventilhülse 28 mit dem Ventilsitz 31 und andererseits durch die Länge des Steuerschiebers 27 vorgegeben ist.In the closed position, the valve ball 16 is pressed by the spring 30 against the valve seat 31. In this position, the valve ball 16 is at a certain distance from the end face 32 of the control slide 27, which is predetermined on the one hand by the dimensions of the valve sleeve 28 with the valve seat 31 and on the other hand by the length of the control slide 27.

Bei Druckaufbau auf der Druckseite wird die Ventilkugel 16 aus ihrem Ventilsitz 31 gegen die Kraft der Feder 30 in Richtung des Pfeiles 35 auf die Stirnseite 32 des Steuerschiebers 27 zu verschoben und damit das Bypassventil 16, 30,31,36 geöffnet. Ein Druckausgleich kann nun von der Hochdruckseite durch die Bypassleitung über die Austrittsöffnung 29 der Ventilhülse 28 in die Saugleitungen bzw. Niederdruckleitungen stattfinden. Bei zunehmendem Druckaufbau auf der Druckseite wird die Ventilkugel 16 schließlich gegen die Stirnseite 32 des Steuerschiebers 27 gedrückt. Gleichzeitig weicht jedoch auch der Steuerschieber 27 gegen die Vorspannung der Feder 30 zurück, bis schließlich, nachdem der eingestellte Maximaldruck erreicht ist, die Ventilkugel 16 in dem Ventilsitz 36 zu Liegen kommt und das Bypassventil schließt.When pressure builds up on the pressure side, the valve ball 16 is displaced from its valve seat 31 against the force of the spring 30 in the direction of arrow 35 toward the end face 32 of the control slide 27, and the bypass valve 16, 30, 31, 36 is thus opened. A pressure equalization can now take place from the high pressure side through the bypass line via the outlet opening 29 of the valve sleeve 28 into the suction lines or low pressure lines. With increasing pressure build-up on the pressure side, the valve ball 16 is finally pressed against the end face 32 of the control slide 27. At the same time, however, the control slide 27 also backs up against the bias of the spring 30 until finally, after the set maximum pressure has been reached, the valve ball 16 comes to rest in the valve seat 36 and the bypass valve closes.

Sinkt dagegen der Druck auf der Druckseite wieder ab, wird die Ventilkugel 16 zunächst durch die Kraft der Feder 30 aus dem Ventilsitz 36 gehoben und in Richtung des Ventilsitzes 31 gedrückt. Das Bypassventil 16,30,31,36 ist nun wieder geöffnet und es kann ein Druckausgleich von der Druckseite durch die Bypassleitung hin zu den Niederdruckleitungen stattfinden. Mit diesem Druckausgleich nimmt gleichzeitig auch die auf die Ventilkugel 16 wirkende Gegenkraft zu der Kraft der Feder 30 ab, so daß sich die Ventilkugel 16 in Richtung auf den Ventilsitz 31 zubewegt und schließlich an diesem zum Liegen kommt. Damit ist das Bypassventil 16,30,31,36 wieder geschlossen und der Druck auf der Druckseite abgebaut, so daß die Hochdruckpumpe problemlos gestartet werden kann.On the other hand, if the pressure on the pressure side drops again, the valve ball 16 is first lifted out of the valve seat 36 by the force of the spring 30 and pressed in the direction of the valve seat 31. The bypass valve 16, 30, 31, 36 is now open again and pressure equalization can take place from the pressure side through the bypass line to the low pressure lines. With this pressure equalization, the counterforce acting on the valve ball 16 to the force of the spring 30 also decreases, so that the valve ball 16 moved towards the valve seat 31 and finally comes to rest on this. The bypass valve 16, 30, 31, 36 is thus closed again and the pressure on the pressure side is reduced, so that the high-pressure pump can be started without problems.

Bei dem erfindungsgemäßen Druckentlastungsventil nach dieser Ausführungsform kann folglich über die Feder 30 der untere Grenzdruck eingestellt werden, bei dem das Bypassventil 16, 30,31,36 geöffnet werden soll bzw. auf welchen unteren Wert der gewünschte Druckausgleich in der Hochdruckleitung erfolgen soll. Gleichzeitig wird durch die Kraft der Feder 30 der Druckbereich einstellbar, in welchem das Bypassventil 16,30,31,36 geöffnet sein soll, damit eine leitende Verbindung zwischen der Druckseite und der Niederdruckseite hergestellt ist.In the pressure relief valve according to the invention in accordance with this embodiment, the lower limit pressure at which the bypass valve 16, 30, 31, 36 is to be opened or at which lower value the desired pressure equalization in the high-pressure line is to be set can thus be set via the spring 30. At the same time, the pressure range in which the bypass valve 16, 30, 31, 36 is to be opened is adjustable by the force of the spring 30, so that a conductive connection is established between the pressure side and the low pressure side.

Ein zweiter, den Druckbereich bestimmender Parameter, ist der Abstand der beiden Ventilsitze 31 und 36 zueinander, welcher den möglichen Verschiebeweg der Ventilkugel 16 bestimmt.A second parameter determining the pressure range is the distance between the two valve seats 31 and 36, which determines the possible displacement path of the valve ball 16.

Der Arbeitsdruck, welcher nach dem Anlaufvorgang der Hochdruckpumpe auf der Druckseite vorherrschen soll, ist auch bei dieser Ausführungsform nach wie vor durch die Feder 18 des Steuerventils 1 einstellbar. Durch die Kraft der Feder 18 ist nämlich der Wert des erforderlichen Druckes einstellbar, der notwendig ist, um den Steuerschieber 27 in Pfeilrichtung 35 nach oben schieben zu können, damit schließlich die Ventilkugel 16 an dem Ventilsitz 36 anliegt und das Bypassventil 16,30,31,36 nach Erreichen des Arbeitsdruckes schließt.The working pressure which is to prevail on the pressure side after the high-pressure pump has started up can also be adjusted in this embodiment by the spring 18 of the control valve 1. The force of the spring 18 can in fact be used to set the value of the required pressure which is necessary in order to be able to push the control slide 27 upward in the direction of arrow 35, so that finally the valve ball 16 rests on the valve seat 36 and the bypass valve 16, 30, 31 , 36 closes after the working pressure is reached.

Wie bereits aus der obigen Funktionsbeschreibung des Steuerventils mit Bypassventil 16,30,31,36 hervorging, ist es funktionsnotwendig, daß die Federkonstante der Feder 18 größer ist als die Federkonstante der Feder 30.As already emerged from the above functional description of the control valve with bypass valve 16, 30, 31, 36, it is functionally necessary that the spring constant of the spring 18 is greater than the spring constant of the spring 30.

Mit dem erfindungsgemäßen Druck-Saugverteiler ist somit ein Verteiler mit einfachem Aufbau bereitgestellt, welcher einen einwandfreien Anlauf der Hochdruckpumpe bei geschlossener Pistole bzw. bei Unterspannung gewährleistet und darüber hinaus kostengünstig herzustellen ist.With the pressure-suction distributor according to the invention, a distributor with a simple structure is thus provided, which ensures a trouble-free start of the high-pressure pump when the pistol is closed or in the event of undervoltage and, moreover, is inexpensive to manufacture.

Claims (7)

  1. Pressure-suction distributor of a high pressure cleaning apparatus with:
    - a low pressure line (6), in which water is supplied to a high pressure pump;
    - a high pressure line (2, 8), which runs from the high pressure pump up to a spray nozzle;
    - a control valve (1), which is provided along the high pressure line (2, 8), in order to selectively lock or release it; and
    - a bypass valve (9, 10, 11, 12, 13; 16, 30, 31, 36),
    characterised in that
    - the bypass valve (9, 10, 11, 12, 13; 16, 30, 31, 36) is arranged in the direction of flow in front of the control valve (1) along the high pressure line (2, 8) running to the spray nozzle, and connects the high pressure line (2, 8) with the low pressure line (6);
    - the bypass valve (9, 10, 11, 12, 13; 16, 30, 31, 36) is pressure-controlled such that on rising of the pressure it opens a flow path between the high pressure line (2, 8) and the low pressure line (6) and closes this flow path again on reaching a particular increased pressure.
  2. Distributor according to Claim 1, characterised in that the bypass valve (9, 10, 11, 12, 13) is a valve acting bilaterally.
  3. Distributor according to Claim 2, characterised in that the bypass valve has a spring (13) which closes the bypass valve (9, 10, 11, 12, 13) with a determinable force as long as the high pressure prevailing at the bypass valve (9, 10, 11, 12, 13) does not exceed a particular value (22).
  4. Distributor according to Claim 3, characterised in that the elastic force is determined such that as soon as the high pressure prevailing at the bypass valve (9, 10, 11, 12, 13) exceeds an upper value (23), this presses the bypass valve (9, 10, 11, 12, 13) against the force of the spring (13) into a valve seat (12) and thereby closes the bypass valve (9, 10, 11, 12, 13).
  5. Distributor according to one of Claims 3 or 4, characterised in that - when the high pressure pump is working in self-aspirating operation - the bypass valve (9, 10, 11, 12, 13) automatically closes via the spring (13) and thereby prevents the air from being pressed out of the high pressure line (8) into the low pressure line (6).
  6. Distributor according to one of Claims 1 - 5, characterised in that the bypass valve (16, 30, 31, 36) is combined with the control valve (1).
  7. Distributor according to Claim 6, characterised in that the spring (30) is placed onto a free end of a control slider (27) and presses a valve ball (16) at a distance from an end face (32) of the control slider (27) against a valve seat (31) and that the control valve (1) has a valve housing (28) which surrounds the control slider (27) and the spring (30) coaxially with play, in which the internal diameter of the valve sleeve (28) is at least partially smaller than the external diameter of the valve ball (16).
EP94100936A 1993-01-22 1994-01-24 Pressure and suction distributor for high pressure cleaning apparatus with an additional control valve Expired - Lifetime EP0608796B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9300831U DE9300831U1 (en) 1993-01-22 1993-01-22
DE9300831U 1993-01-22

Publications (2)

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EP0608796A1 EP0608796A1 (en) 1994-08-03
EP0608796B1 true EP0608796B1 (en) 1997-06-11

Family

ID=6888437

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Application Number Title Priority Date Filing Date
EP94100936A Expired - Lifetime EP0608796B1 (en) 1993-01-22 1994-01-24 Pressure and suction distributor for high pressure cleaning apparatus with an additional control valve

Country Status (4)

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EP (1) EP0608796B1 (en)
AT (1) ATE154420T1 (en)
DE (2) DE9300831U1 (en)
ES (1) ES2105359T3 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102686882A (en) * 2009-10-01 2012-09-19 阿尔弗雷德·凯驰两合公司 Pump for a high-pressure cleaning device

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5718255A (en) * 1997-01-09 1998-02-17 Generac Corporation Flow-responsive diverting valve
DE102007017970A1 (en) 2007-04-11 2008-10-16 Alfred Kärcher Gmbh & Co. Kg High-pressure cleaner
DE102009049095A1 (en) 2009-10-01 2011-04-07 Alfred Kärcher Gmbh & Co. Kg Pump for a high-pressure cleaning device
DE102009049096A1 (en) 2009-10-01 2011-04-07 Alfred Kärcher Gmbh & Co. Kg Pump for a high-pressure cleaning device
CN102537453B (en) * 2012-01-04 2013-07-03 安徽博一流体传动股份有限公司 Self-operated reducing valve

Family Cites Families (3)

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Publication number Priority date Publication date Assignee Title
DE3313249A1 (en) * 1983-04-13 1984-10-25 Woma-Apparatebau Wolfgang Maasberg & Co Gmbh, 4100 Duisburg HIGH PRESSURE WATER JET SYSTEM
DE3922956A1 (en) * 1989-07-12 1991-01-17 Kaercher Gmbh & Co Alfred HIGH PRESSURE CLEANER
US5035580A (en) * 1989-09-14 1991-07-30 Diversified Dynamics Corporation Bypass mode control for high pressure washing system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102686882A (en) * 2009-10-01 2012-09-19 阿尔弗雷德·凯驰两合公司 Pump for a high-pressure cleaning device

Also Published As

Publication number Publication date
ATE154420T1 (en) 1997-06-15
ES2105359T3 (en) 1997-10-16
DE59403061D1 (en) 1997-07-17
EP0608796A1 (en) 1994-08-03
DE9300831U1 (en) 1993-04-22

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