EP2131970A1 - High-pressure cleaning device - Google Patents

High-pressure cleaning device

Info

Publication number
EP2131970A1
EP2131970A1 EP08735129A EP08735129A EP2131970A1 EP 2131970 A1 EP2131970 A1 EP 2131970A1 EP 08735129 A EP08735129 A EP 08735129A EP 08735129 A EP08735129 A EP 08735129A EP 2131970 A1 EP2131970 A1 EP 2131970A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
cleaning device
outlet
channel
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.)
Granted
Application number
EP08735129A
Other languages
German (de)
French (fr)
Other versions
EP2131970B1 (en
Inventor
Wolfgang Müller
Sven Dirnberger
Bernd KÖRNER
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alfred Kaercher SE and Co KG filed Critical Alfred Kaercher SE and Co KG
Publication of EP2131970A1 publication Critical patent/EP2131970A1/en
Application granted granted Critical
Publication of EP2131970B1 publication Critical patent/EP2131970B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B3/00—Cleaning by methods involving the use or presence of liquid or steam
    • B08B3/02—Cleaning by the force of jets or sprays
    • B08B3/026—Cleaning by making use of hand-held spray guns; Fluid preparations therefor
    • 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 high-pressure cleaning device having a high-pressure pump, which has at least one pump chamber which is connected to a suction line and a pressure line, wherein the pressure line via a return line to the suction line is in flow communication and in the return line a relief valve is arranged, wherein the relief valve a Through passageway which extends from a valve inlet to a first valve outlet and which forms a valve seat, downstream of the valve seat from the passage at least one outlet channel branches off, which opens into a second valve outlet, and wherein in the passageway a valve element is movably supported by means of a Return spring to the valve seat is sealingly applied.
  • Such high-pressure cleaning devices are known from DE 297 12 659 Ul. With their help, a surface to be cleaned with pressurized cleaning liquid, for example, with water, are applied.
  • a high-pressure hose can be connected to the pressure line, which carries at its free end, for example, a spray lance for spraying the surface to be cleaned.
  • cleaning fluid can be supplied to the pump chamber via the suction line, which is pressurized within the pump chamber is, for example, with the help of a plunging into the pump chamber and rezirprotropicd sliding piston.
  • the pressurized cleaning fluid can then be passed via the pressure line to a consumer.
  • the relief valve In this operating state, the relief valve is in its closed position, so that the direct connection between the pressure line and the suction line is interrupted via the return line.
  • the relief valve When a certain pressure value within the pressure line, as he adjusts, for example, when closing a spray lance connected to the free end of the high-pressure hose, the relief valve goes into its open position by the valve member lifts off from the valve seat against the restoring force exerted by the return spring, so that Cleaning liquid can flow back directly from the pressure line via the return line through the discharge valve to the suction line and thereby degrades the pressure in the pressure line.
  • the decrease in pressure can result in the valve element being pushed back onto the valve seat by the return spring shortly after it has been lifted off the valve seat, in order then to lift it off the valve seat again.
  • the transition of the relief valve from the closed position to the open position of the relief valve can thus be connected to a swinging movement of the valve element and the return spring. This oscillating movement represents a considerable mechanical load. This can lead to a malfunction of the high-pressure cleaner.
  • Object of the present invention is to develop a high-pressure cleaning device of the type mentioned in such a way that it is CADsunan Universityer.
  • This object is achieved according to the invention in a high-pressure cleaning device of the generic type in that the valve element in the direction away from the valve seat is surrounded by a sealing ring spaced from the at least one outlet channel, which has an inlet region of the passage channel adjacent to the valve inlet of an end region adjacent to the first valve outlet the passageway seals.
  • the relief valve changes into its open position, in which the valve element lifts off from the valve seat.
  • the flow connection is released between the valve inlet and the second valve outlet, so that cleaning liquid can flow through the inlet area of the passage channel through the at least one outlet channel to the second valve outlet.
  • the valve element In the inlet region of the through-channel, ie in the region of the through-channel between the valve inlet and the sealing ring, the valve element is thus subject to a considerable pressure load.
  • the valve element experiences a considerably lower pressure load.
  • the consequently acting on the valve element pressure difference has the consequence that the tendency of the valve element to vibrate is greatly reduced.
  • the risk of a spring break, caused by an unintentional oscillation movement of the valve element, can thereby be significantly reduced.
  • the high-pressure cleaner according to the invention is therefore characterized by a low susceptibility to interference.
  • the opening force acting on the valve element in the open position of the relief valve which results from the above-explained pressure difference, is dependent on the size of the sealed area defined by the sealing ring.
  • the opening force can be influenced by the choice of the area size.
  • the liquid flowing into the relief valve can flow back into the suction line from the pressure line of the high-pressure cleaner when a pressure peak occurs.
  • Cleaning liquid which can happen in the event of a leak, the sealing element surrounding the valve element, can flow out of the relief valve via the first valve outlet.
  • the first valve outlet thus forms a leakage opening.
  • it allows a pressure equalization between the pressure prevailing in the suction line pressure and the pressure in the outlet region of the through-channel. After the reduction of the pressure peak in the pressure line, the relief valve automatically returns to its closed position due to the force acting on the valve element restoring force of the return spring.
  • the sealing ring can be arranged, for example, in a groove machined into the wall of the through-channel, and the valve element can be reciprocable relative to the sealing ring, the sealing ring sealingly bearing against the circumference of the valve element.
  • the sealing ring is arranged in a circumferential groove of the valve element.
  • the inner diameter of the sealing ring is greater than the diameter of the bottom of the circumferential groove of the valve element. This has the consequence that the sealing ring is indeed received by the circumferential groove, but with its inner edge is not applied to the bottom of the circumferential groove.
  • a sealing abutment is present between the outer edge of the sealing ring and the wall of the through-channel. It has been shown that thereby the valve element can be held more easily movable in the passageway.
  • valve element has a closing body, which is sealingly engageable with the valve seat, and a pressure body which is surrounded by the sealing ring at a distance from the closing body.
  • the closing body may be designed, for example, spherical or conical. Closing body and pressure body can be materially connected to each other, in particular it can be provided that the closing body and the pressure body form an integrally ausgestaltetes valve element.
  • the passage channel comprises a guide portion, on the inner wall of the pressure body is slidably mounted with the interposition of the sealing ring.
  • the guide section forms a sliding guide for the valve element and provides on its inner wall the sealing surface associated with the sealing surface.
  • the relief valve so gradually assumes its closed position, starting from its open position, in which the valve element reseals sealingly against the valve seat, it is advantageous if the flow cross-section of the Gangskanals in the region upstream of the at least one outlet channel is greater than the flow cross-section of the outlet channel.
  • the exhaust passage thus forms a throttle element so that a substantial pressure is established upstream of the exhaust passage when the relief valve assumes its open position.
  • the flow of the cleaning fluid entering the relief valve is subject to a resistance in the area of the decreasing flow cross-section, so that the pressure prevailing in the inlet region of the through-channel is very gradually reduced.
  • the relief valve has a single outlet channel, because this allows the manufacturing cost of the relief valve can be kept low and by means of the single outlet channel, a considerable throttle effect can be generated.
  • valve element at least partially releases the at least one outlet channel both in the open position and in the closed position of the relief valve.
  • Such a configuration has the effect that, when the valve element is lifted off the valve seat, a continuous flow connection from the valve inlet via the inlet region of the passage channel and the outlet channel to the second valve outlet is ensured immediately, ie inflowing liquid can flow through the relief valve even with a slight lift-off movement of the valve element from the valve seat, it is not necessary that the valve member occupy a minimum distance to the valve seat, to release the flow connection between the valve inlet and the second valve outlet.
  • the valve element is associated with a stop on which the valve element rests in the open position of the relief valve. The stop forms a defined stroke limitation for the valve element, so that the desired stroke of the valve element can be structurally predetermined by the position of the stop.
  • the stop is formed by a constriction of the through-channel.
  • the passageway may, for example, form a step at which the valve element may rest in the open position of the relief valve.
  • the stop is formed by a support element arranged in the through-channel.
  • a support element arranged in the through-channel.
  • the support member is in a preferred embodiment radially inwardly from an inner wall of the passageway.
  • the relief valve has a first housing part and a second housing part, which can be connected to one another with the interposition of a sealing ring.
  • a detachable or even a permanent connection for example a latching or screw connection, can be used.
  • the first housing part preferably comprises the valve inlet, the valve seat and the at least one outlet channel and the second valve outlet, and the second housing part preferably has the first valve outlet.
  • the second housing part comprises an insert which can be inserted with the interposition of a sealing ring in the first housing part. It is advantageous if the insert carries on the outside an annular groove in which the sealing ring is arranged.
  • the insert may be, for example, cup-shaped and receive the end of the valve element facing away from the valve seat. In this end region, the valve element may have an annular groove in which the sealing ring surrounding the valve element is arranged.
  • the return spring is preferably clamped between a collar of the valve element and an end face of the second housing part.
  • Figure 1 a schematic side view of a high-pressure cleaning device according to the invention
  • FIG. 2 is an enlarged longitudinal sectional view of the pump head of the high-pressure cleaning device from FIG. 1;
  • FIG. 3 shows a longitudinal sectional view of a first embodiment of a relief valve of the high-pressure cleaning device from FIG. 1 and
  • FIG. 4 shows a longitudinal sectional view of a second embodiment of a relief valve of the high-pressure cleaning device from FIG. 1.
  • FIGS. 1 and 2 schematically show a high-pressure cleaning device 10 with a device housing 12 which accommodates a motor pump unit 14.
  • the latter includes an electric motor 15, an adjoining gear 16 and a driven via a swash plate 17 piston pump 18 with a plurality of reciprocating in the axial direction of the high-pressure cleaner 10 reciprocating piston 19.
  • These dive into a pump chamber 21 of a pump head 22 of the high-pressure cleaner 10 a.
  • the pump chambers 21 are each connected via a suction valve 24 to a suction line 25 and via a pressure valve 27 to a pressure line 28.
  • the suction line 25 and the pressure line 28 are all pump chambers 21 of the pump head 22 together.
  • a spring-loaded check valve 30 is used, in the flow direction of the flow cross-section of the pressure line 28 reducing injector 31 connects, which is connected at its narrowest point via a suction channel 32 with a Chemikalienansaug effet 33, which is closed by a check valve 34 ,
  • check valve 30 and the injector 31 performs a gradually expanding in the flow direction remind 36 from the pressure line 28 directly to the suction line 25.
  • the circumferentially is surrounded by a sealing ring 39 which applies sealingly against the wall of the return line 36.
  • the relief valve 38 is shown enlarged in FIG. It comprises a two-part housing with a first housing part 41 which carries the sealing ring 39 in a circumferential groove 42 and can be inserted sealed into the return flow line 36.
  • the relief valve 38 comprises a second, cup-shaped housing part 44 with a cylindrical jacket 45 and a bottom wall 46.
  • the second housing part 44 is latched to the first housing part 41.
  • the first housing part 41 at its circumferential groove 42 remote from the end an annular groove 48 into which an inwardly projecting annular shoulder 49 of the second housing part 44 can engage elastically when the second housing part 44 is pushed in the axial direction on the first housing part 41.
  • the two housing parts 41 and 44 define a through-channel 50 which, starting from a front-side valve inlet 52, forms a first channel section 53, which merges via a spherical extension 54 into a second channel section 56.
  • the extension 54 forms a valve seat 58 for the closing body 60 of a longitudinally of the passage channel 50 movably held in the passage 50 valve member 61.
  • the closing body 60 is configured in the form of a spherical cap and is in the closed position shown in Figure 3 of the relief valve 38 sealingly against the valve seat 58 on. In the axial direction, a pressure body 63 of the valve element 61 connects to the closing body 60.
  • the pressure body 63 is designed in the form of a piston and carries on the outside a circumferential groove 64, in which a sealing element 66 surrounding the valve element 61 in the circumferential direction is arranged.
  • the sealing ring 66 abuts against the wall of the through-channel 50 in the region of its second channel section 56.
  • a third channel section 69 Connected to the second channel section 56 in the axial direction via a conical extension 68 is a third channel section 69, which merges via a stepped extension 71 into a fourth channel section 72.
  • the fourth channel section 72 is defined by the jacket 45 of the second housing part 44. It has in the axial direction extending and radially from the jacket 45 inwardly projecting longitudinal ribs 74, which extend to the bottom wall 46 by cross-first valve outlets 75.
  • the fourth channel section 72 accommodates a return spring 77 configured as a helical spring, which is supported on the bottom wall 46 of the second housing part 44 on the one hand and on the underside 78 of the pressure body 63 facing the bottom wall 46 on the other hand.
  • a return spring 77 configured as a helical spring, which is supported on the bottom wall 46 of the second housing part 44 on the one hand and on the underside 78 of the pressure body 63 facing the bottom wall 46 on the other hand.
  • the upper, the pressure body 63 facing end face 80 of the longitudinal ribs 74 forms a stop for the pressure body 63 of the valve member 61 when it lifts in the open position of the relief valve 38 from the valve seat 58. This will be explained in more detail below.
  • the first housing part 41 has, at a distance from the valve seat 58 in the second passage section 56 of the passage channel 50, a radially extending exhaust port. channel 88, whose radially outer end region forms a second valve outlet 89 of the relief valve 38.
  • the sealing ring 66 surrounding the valve element 61 in the circumferential direction divides the through-passage 50 into an inlet region 91 and an outlet region 92.
  • the inlet region 91 is formed by the first channel section 53, the spherical extension 54 and the region of the second channel section 56 surrounding the closing body 60.
  • the outlet region 92 is formed by the area adjoining the closing body 60 of the second channel section 56, the conical extension 68, the third channel section 69 and the stepped extension 71 and the fourth channel section 72.
  • valve element 61 is pressed by the return spring 77 against the valve seat 58, so that the relief valve 38 assumes its closed position, in the flow connection from the valve inlet 52 via the inlet region 91 of the through-channel 50 and the outlet channel 88 to the second valve outlet 89 is interrupted.
  • valve member 61 When exceeding a certain pressure value of the cleaning liquid, as may occur, for example, when switching off the high-pressure cleaner 10, the valve member 61 is lifted against the spring force of the return spring 77 from the valve seat 58 and moved in the valve seat 58 facing away from the direction down to the pressure body 63 with its bottom 78 abuts against the free end face 80 of the longitudinal ribs 74.
  • valve element 61 in the open position of the relief valve 38 acts on the valve element 61, a pressure difference, which has the consequence that the valve element 61 is acted upon by an axially against the action of the return spring 77 acting force, the valve member 61 reliably as long as the distance from the valve seat 58 holds until the pressure of the cleaning liquid in the inlet region 91 has lowered so far that the force of the return spring 77 is sufficient to return the valve element to the valve seat 58.
  • the pressure difference acting on the valve element 61 in the open position of the relief valve 38 reduces the occurrence of oscillatory movements of the valve element 61.
  • the relief valve 98 has a first housing part 101 and a second housing part 102. On the outside, the first housing part 101 carries a circumferential groove 104, which receives a sealing ring 105 which abuts sealingly against the wall of the return flow line 36 in the return flow line 36 when the relief valve 98 designed as a self-contained cartridge is inserted.
  • the housing parts 101 and 102 are locked together.
  • a screw connection for detachably connecting the two housing parts 101, 102 could be used.
  • the two housing parts 101 and 102 define a passage 107. This proceeds from a front-side valve inlet 109 of the first housing part 101 and extends with a first cylindrical channel portion 111 to a first conical extension 112, which is followed by a second cylindrical channel portion 113, which merges via a second conical extension 114 in a third cylindrical channel section 115.
  • the third cylindrical channel section 115 is surrounded by a jacket 117 of the first housing part 101.
  • the second housing part 102 dives with a cup-shaped insert 119, which defines a fourth cylindrical channel portion 120 of the passage channel 107.
  • the insert 119 is integrally connected to a bottom wall 122 of the second housing part 102, which closes the free end of the shell 117 of the first housing part 101.
  • a cylindrical extension 123 On the side facing away from the insert 119 connects to the bottom wall 122, a cylindrical extension 123, which is like the bottom wall 122 penetrated by an axially extending through hole 124.
  • the through-bore 124 forms a fifth cylindrical passage section 125 of the through-passage 107, a stepped narrowing 126 being arranged in the transitional area between the fourth passage section 120 and the fifth passage section 125.
  • the cup-shaped insert 119 carries on its outer side an annular groove 129, in which a sealing ring 130 is arranged, which ensures a liquid-tight connection between the first housing part 101 and the second housing part 102.
  • a valve member 132 is movably mounted with a designed in the form of a spherical cap closing body 133 and an axially adjoining this pressure body 134.
  • the closing body 133 is in the closed position shown in Figure 4 of the relief valve 98 at one of the first conical extension 112 formed valve seat 136 tightly.
  • the pressure body 134 extends from the closing body 133 into the region of the fourth channel section 120, where it bears on the outside an annular groove 138 in which a sealing ring 139 surrounding the valve element 132 in the circumferential direction is arranged.
  • the inner diameter of the sealing ring is selected larger than the diameter of the bottom of the annular groove 138. This has the consequence that the sealing ring 139 is at a distance from the bottom of the annular groove 138, as shown in Figure 4. On the outside, the sealing ring 139 is tight against the wall of the fourth channel section 120.
  • the pressure body 134 has a collar 144 below the longitudinal axis 141 of a radially extending outlet channel 142.
  • a restoring spring 146 which surrounds the pressure body 134 in the third channel section 115 in the circumferential direction and is designed as a helical spring, is braced, on the one hand, on the free end face 148 of the cup-shaped insert 119 facing the valve seat 136 and on the other side on the underside 149 of the collar 144 facing away from the valve seat 136.
  • the return spring 146 By means of the return spring 146, the valve element 132 is acted upon by a spring force in the direction of the valve seat 136.
  • the fifth channel section 125 extending through the bottom wall 122 and the axial extension 123 forms with its free end region a first valve outlet 151, and the outlet channel 142 emanating from the through-channel 107 forms with its radially outer end region a second valve outlet 152.
  • the passage 107 becomes the valve element 132 circumferentially surrounding sealing ring 139 into an inlet portion 154 and an outlet portion 155, which are separated by the sealing ring 139 liquid-tight from each other.
  • the inlet region 154 is formed by the first channel section 111, the first conical extension 112, the second channel section 113, the second conical extension 114, the third channel section 115 and the part of the fourth channel section 120 which is adjacent to the free end side 148.
  • the outlet region 155 of the through-channel 107 is formed by the portion of the fourth channel section 120 adjacent to the stepped constriction 126 and the fifth channel section 125.
  • the relief valve 98 assumes its closed position, in which the valve element 132 bears tightly against the valve seat 136 with the closing body 133.
  • the valve element 132 is lifted against the force of the return spring 146 from the valve seat 136 until the pressure element 134 abuts with its end facing away from the closing body 133 at the stepped constriction 126.
  • the stepped constriction 126 thus forms a stop to limit the Strokes of the valve element 132 from.
  • valve element 132 By lifting the valve element 132 from the valve seat 136, a flow connection from the valve inlet 107 to the second valve outlet 152 is released so that excess liquid can escape from the pressure line 28 via the return line 36 to the suction line 25.
  • a considerable pressure arises in the inlet region 154 of the through-channel 107, whereas in the outlet region 155 a considerably lower pressure is present, namely the pressure prevailing in the suction line 25.
  • a differential pressure acts on the valve element 132, which results in a force application facing away from the valve seat 136. Due to this application of force, the valve element 132 retains its position spaced from the valve seat 136 until the overpressure in the pressure line 28 has decreased.
  • the pressure reduction takes place gradually, since the flow cross-section of the outlet channel 142 is selected smaller than the flow cross-section of the passage channel upstream of the outlet channel 142.
  • the latter forms a throttle element for the cleaning fluid flowing through the relief valve 98, which ensures that in the inlet region 154 of the through-channel 107 a builds considerable pressure when the relief valve 98 assumes its open position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Cleaning In General (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Control Of Fluid Pressure (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Centrifugal Separators (AREA)
  • Cleaning By Liquid Or Steam (AREA)

Abstract

The invention relates to a high-pressure cleaning device comprising a high-pressure pump, which has at least one pump chamber that is connected to a suction line and to a pressure line. The pressure line is flow connected to the suction line via a return flow line, and a pressure relief valve is disposed in the return flow line, the valve having a through-flow channel extending from a valve inlet to a first valve outlet. A valve element is movably held in the through-flow channel, the element ending in a closed position on a valve seat. At least one outlet channel branches off from the through-flow channel, the channel ending in a second valve outlet. In order to configure the high-pressure cleaning device less prone to failure, the invention provides that the valve element is enclosed by a sealing ring at a distance to at least one outlet channel in the direction opposite of the valve seat, wherein the sealing ring seals an inlet region of the through-flow channel adjacent to the valve inlet from an outlet region of the through-flow channel adjacent to the first valve outlet.

Description

Hochdruckreinigungsgerät High-pressure cleaner
Die Erfindung betrifft ein Hochdruckreinigungsgerät mit einer Hochdruckpumpe, die mindestens einen Pumpraum aufweist, der mit einer Saugleitung und einer Druckleitung verbunden ist, wobei die Druckleitung über eine Rückströmleitung mit der Saugleitung in Strömungsverbindung steht und in der Rückströmleitung ein Entlastungsventil angeordnet ist, wobei das Entlastungsventil einen Durchgangskanal umfasst, der sich von einem Ventileinlass zu einem ersten Ventilauslass erstreckt und der einen Ventilsitz ausbildet, wobei stromabwärts des Ventilsitzes vom Durchgangskanal mindestens ein Auslasskanal abzweigt, der in einen zweiten Ventilauslass einmündet, und wobei im Durchgangskanal ein Ventilelement beweglich gehalten ist, das mittels einer Rückstellfeder an den Ventilsitz dichtend anlegbar ist.The invention relates to a high-pressure cleaning device having a high-pressure pump, which has at least one pump chamber which is connected to a suction line and a pressure line, wherein the pressure line via a return line to the suction line is in flow communication and in the return line a relief valve is arranged, wherein the relief valve a Through passageway which extends from a valve inlet to a first valve outlet and which forms a valve seat, downstream of the valve seat from the passage at least one outlet channel branches off, which opens into a second valve outlet, and wherein in the passageway a valve element is movably supported by means of a Return spring to the valve seat is sealingly applied.
Derartige Hochdruckreinigungsgeräte sind aus der DE 297 12 659 Ul bekannt. Mit ihrer Hilfe kann eine zu reinigende Fläche mit unter Druck stehender Reinigungsflüssigkeit, beispielsweise mit Wasser, beaufschlagt werden. Hierzu kann an die Druckleitung ein Hochdruckschlauch angeschlossen werden, der an seinem freien Ende beispielsweise eine Sprühlanze trägt zum Besprühen der zu reinigenden Fläche.Such high-pressure cleaning devices are known from DE 297 12 659 Ul. With their help, a surface to be cleaned with pressurized cleaning liquid, for example, with water, are applied. For this purpose, a high-pressure hose can be connected to the pressure line, which carries at its free end, for example, a spray lance for spraying the surface to be cleaned.
Im Normalbetrieb kann dem Pumpraum über die Saugleitung Reinigungsflüssigkeit zugeführt werden, die innerhalb des Pumpraums unter Druck gesetzt wird, beispielsweise mit Hilfe eines in den Pumpraum eintauchenden und rezi- prozierend verschiebbaren Kolbens. Die unter Druck gesetzte Reinigungsflüssigkeit kann dann über die Druckleitung zu einem Verbraucher geführt werden. In diesem Betriebszustand befindet sich das Entlastungsventil in seiner Schließstellung, so dass die direkte Verbindung zwischen der Druckleitung und der Saugleitung über die Rückströmleitung unterbrochen ist. Bei Überschreiten eines bestimmten Druckwertes innerhalb der Druckleitung, wie er sich beispielsweise beim Verschließen einer am freien Ende des Hochdruckschlauchs angeschlossenen Sprühlanze einstellt, geht das Entlastungsventil in seine Offenstellung über, indem sich das Ventilelement entgegen der von der Rückstellfeder ausgeübten Rückstellkraft vom Ventilsitz abhebt, so dass Reinigungsflüssigkeit direkt von der Druckleitung über die Rückströmleitung durch das Entlastungsventil hindurch zur Saugleitung zurückströmen kann und sich dadurch der Druck in der Druckleitung abbaut. Die Druckabnahme kann zur Folge haben, dass das Ventilelement kurz nach Abheben vom Ventilsitz von der Rückstellfeder wieder auf den Ventilsitz zurückgedrückt wird, um dann erneut vom Ventilsitz abzuheben. Der Übergang des Entlastungsventils von der Schließstellung zur Offenstellung des Entlastungsventils kann somit mit einer schwingenden Bewegung des Ventilelements und der Rückstellfeder verbunden sein. Diese schwingende Bewegung stellt eine erhebliche mechanische Belastung dar. Dies kann zu einer Störung des Hochdruckreinigungsgeräts führen.In normal operation, cleaning fluid can be supplied to the pump chamber via the suction line, which is pressurized within the pump chamber is, for example, with the help of a plunging into the pump chamber and rezirprozierend sliding piston. The pressurized cleaning fluid can then be passed via the pressure line to a consumer. In this operating state, the relief valve is in its closed position, so that the direct connection between the pressure line and the suction line is interrupted via the return line. When a certain pressure value within the pressure line, as he adjusts, for example, when closing a spray lance connected to the free end of the high-pressure hose, the relief valve goes into its open position by the valve member lifts off from the valve seat against the restoring force exerted by the return spring, so that Cleaning liquid can flow back directly from the pressure line via the return line through the discharge valve to the suction line and thereby degrades the pressure in the pressure line. The decrease in pressure can result in the valve element being pushed back onto the valve seat by the return spring shortly after it has been lifted off the valve seat, in order then to lift it off the valve seat again. The transition of the relief valve from the closed position to the open position of the relief valve can thus be connected to a swinging movement of the valve element and the return spring. This oscillating movement represents a considerable mechanical load. This can lead to a malfunction of the high-pressure cleaner.
Aufgabe der vorliegenden Erfindung ist es, ein Hochdruckreinigungsgerät der eingangs genannten Art derart weiterzubilden, dass es störungsunanfälliger ist. Diese Aufgabe wird bei einem Hochdruckreinigungsgerät der gattungsgemäßen Art erfindungsgemäß dadurch gelöst, dass das Ventilelement in der dem Ventilsitz abgewandten Richtung im Abstand zu dem mindestens einen Auslasskanal von einem Dichtring umgeben ist, der einen dem Ventileinlass benachbarten Einlassbereich des Durchgangskanals von einem dem ersten Ventilauslass benachbarten Endbereich des Durchgangskanals abdichtet.Object of the present invention is to develop a high-pressure cleaning device of the type mentioned in such a way that it is störungsunanfälliger. This object is achieved according to the invention in a high-pressure cleaning device of the generic type in that the valve element in the direction away from the valve seat is surrounded by a sealing ring spaced from the at least one outlet channel, which has an inlet region of the passage channel adjacent to the valve inlet of an end region adjacent to the first valve outlet the passageway seals.
Wie bereits erwähnt, geht das Entlastungsventil bei Auftreten einer Druckspitze in der Druckleitung in seine Offenstellung über, bei der sich das Ventilelement vom Ventilsitz abhebt. Dadurch wird die Strömungsverbindung freigegeben zwischen dem Ventileinlass und dem zweiten Ventilauslass, so dass Reinigungsflüssigkeit durch den Einlassbereich des Durchgangskanals hindurch über den mindestens einen Auslasskanal zum zweiten Ventilauslass strömen kann. Im Einlassbereich des Durchgangskanals, d. h. im Bereich des Durchgangskanals zwischen dem Ventileinlass und dem Dichtring, unterliegt somit das Ventilelement einer beachtlichen Druckbelastung. Auf der diesem Bereich abgewandten Seite des Dichtrings, nämlich innerhalb des Auslassbereichs des Durchgangskanals, erfährt das Ventilelement dagegen eine beträchtlich geringere Druckbelastung. Die folglich auf das Ventilelement einwirkende Druckdifferenz hat zur Folge, dass die Schwingungsneigung des Ventilelementes stark vermindert ist. Der Einsatz des Dichtringes, der den Einlassbereich des Durchgangskanals von dessen Auslassbereich abdichtet, hat somit zur Folge, dass die mechanische Belastung des Ventilelementes und der Rückstellfeder reduziert werden kann. Die Gefahr eines Federbruches, verursacht durch eine unbeabsichtigte Schwingungsbewegung des Ventilelementes, kann dadurch deutlich verringert werden. Das erfindungsgemäße Hochdruckreinigungsgerät zeichnet sich daher durch eine geringe Störungsanfälligkeit aus. As already mentioned, when a pressure peak occurs in the pressure line, the relief valve changes into its open position, in which the valve element lifts off from the valve seat. Thereby, the flow connection is released between the valve inlet and the second valve outlet, so that cleaning liquid can flow through the inlet area of the passage channel through the at least one outlet channel to the second valve outlet. In the inlet region of the through-channel, ie in the region of the through-channel between the valve inlet and the sealing ring, the valve element is thus subject to a considerable pressure load. In contrast, on the side of the sealing ring facing away from this region, namely within the outlet region of the through-channel, the valve element experiences a considerably lower pressure load. The consequently acting on the valve element pressure difference has the consequence that the tendency of the valve element to vibrate is greatly reduced. The use of the sealing ring, which seals the inlet region of the passage channel from its outlet region, thus has the consequence that the mechanical loading of the valve element and the return spring can be reduced. The risk of a spring break, caused by an unintentional oscillation movement of the valve element, can thereby be significantly reduced. The high-pressure cleaner according to the invention is therefore characterized by a low susceptibility to interference.
Die auf das Ventilelement in der Offenstellung des Entlastungsventils einwirkende Öffnungskraft, die aus der voranstehend erläuterten Druckdifferenz resultiert, ist von der Größe der vom Dichtring definierten abgedichteten Fläche abhängig. Somit kann durch die Wahl der Flächengröße die Öffnungskraft be- einflusst werden.The opening force acting on the valve element in the open position of the relief valve, which results from the above-explained pressure difference, is dependent on the size of the sealed area defined by the sealing ring. Thus, the opening force can be influenced by the choice of the area size.
Über den mindestens einen Auslasskanal und den zweiten Ventilauslass kann die in das Entlastungsventil einströmende Flüssigkeit bei Auftreten einer Druckspitze von der Druckleitung des Hochdruckreinigers in die Saugleitung zurückströmen. Reinigungsflüssigkeit, die im Falle einer Undichtigkeit den das Ventilelement umgebenden Dichtring passieren kann, kann über den ersten Ventilauslass aus dem Entlastungsventil herausströmen. Der erste Ventilauslass bildet somit eine Leckageöffnung. Außerdem ermöglicht er einen Druckausgleich zwischen dem in der Saugleitung herrschenden Druck und dem Druck im Auslassbereich des Durchgangskanals. Nach dem Abbau der Druckspitze in der Druckleitung geht das Entlastungsventil aufgrund der auf das Ventilelement einwirkenden Rückstellkraftkraft der Rückstellfeder selbsttätig wieder in seine Schließstellung über.Via the at least one outlet channel and the second valve outlet, the liquid flowing into the relief valve can flow back into the suction line from the pressure line of the high-pressure cleaner when a pressure peak occurs. Cleaning liquid, which can happen in the event of a leak, the sealing element surrounding the valve element, can flow out of the relief valve via the first valve outlet. The first valve outlet thus forms a leakage opening. In addition, it allows a pressure equalization between the pressure prevailing in the suction line pressure and the pressure in the outlet region of the through-channel. After the reduction of the pressure peak in the pressure line, the relief valve automatically returns to its closed position due to the force acting on the valve element restoring force of the return spring.
Der Dichtring kann beispielsweise in einer in die Wandung des Durchgangskanals eingearbeiteten Nut angeordnet sein und das Ventilelement kann relativ zum Dichtring hin- und herbeweglich sein, wobei der Dichtring dichtend am Umfang des Ventilelementes anliegt.The sealing ring can be arranged, for example, in a groove machined into the wall of the through-channel, and the valve element can be reciprocable relative to the sealing ring, the sealing ring sealingly bearing against the circumference of the valve element.
Alternativ kann vorgesehen sein, dass der Dichtring in einer Umfangsnut des Ventilelementes angeordnet ist. Bei einer derartigen Ausgestaltung ist es von Vorteil, wenn der Innendurchmesser des Dichtringes größer ist als der Durchmesser des Bodens der Umfangsnut des Ventilelementes. Dies hat nämlich zur Folge, dass der Dichtring von der Umfangsnut zwar aufgenommen wird, mit seinem Innenrand aber nicht am Boden der Umfangsnut anliegt. Eine dichtende Anlage liegt aber zwischen dem Außenrand des Dichtrings und der Wandung des Durchgangskanals vor. Es hat sich gezeigt, dass dadurch das Ventilelement leichtgängiger im Durchgangskanal beweglich gehalten werden kann.Alternatively it can be provided that the sealing ring is arranged in a circumferential groove of the valve element. In such an embodiment, it is of Advantage, when the inner diameter of the sealing ring is greater than the diameter of the bottom of the circumferential groove of the valve element. This has the consequence that the sealing ring is indeed received by the circumferential groove, but with its inner edge is not applied to the bottom of the circumferential groove. However, a sealing abutment is present between the outer edge of the sealing ring and the wall of the through-channel. It has been shown that thereby the valve element can be held more easily movable in the passageway.
Von Vorteil ist es, wenn das Ventilelement einen Schließkörper aufweist, der am Ventilsitz dichtend anlegbar ist, sowie einen Druckkörper, der im Abstand zum Schließkörper vom Dichtring umgeben ist. Der Schließkörper kann beispielsweise kugelig oder konisch ausgestaltet sein. Schließkörper und Druckkörper können stoffschlüssig miteinander verbunden sein, insbesondere kann vorgesehen sein, dass der Schließkörper und der Druckkörper ein einstückig ausgestaltetes Ventilelement ausbilden.It is advantageous if the valve element has a closing body, which is sealingly engageable with the valve seat, and a pressure body which is surrounded by the sealing ring at a distance from the closing body. The closing body may be designed, for example, spherical or conical. Closing body and pressure body can be materially connected to each other, in particular it can be provided that the closing body and the pressure body form an integrally ausgestaltetes valve element.
Bei einer bevorzugten Ausgestaltung der Erfindung umfasst der Durchgangskanal einen Führungsabschnitt, an dessen Innenwand der Druckkörper unter Zwischenlage des Dichtringes verschiebbar gelagert ist. Der Führungsabschnitt bildet eine Gleitführung für das Ventilelement aus und stellt an seiner Innenwand die dem Dichtring zugeordnete Dichtfläche bereit.In a preferred embodiment of the invention, the passage channel comprises a guide portion, on the inner wall of the pressure body is slidably mounted with the interposition of the sealing ring. The guide section forms a sliding guide for the valve element and provides on its inner wall the sealing surface associated with the sealing surface.
Um sicherzustellen, dass bei Auftreten einer Druckspitze in der Druckleitung der gewünschte Druckabbau eine gewisse Zeit in Anspruch nimmt, das Entlastungsventil also ausgehend von seiner Offenstellung nur allmählich seine Schließstellung einnimmt, in der das Ventilelement wieder dichtend am Ventilsitz anliegt, ist es von Vorteil, wenn der Strömungsquerschnitt des Durch- gangskanals im Bereich stromaufwärts des mindestens einen Auslasskanals größer ist als der Strömungsquerschnitt des Auslasskanals. Der Auslasskanal bildet somit ein Drosselelement aus, so dass sich stromaufwärts des Auslasskanals ein beträchtlicher Druck einstellt, wenn das Entlastungsventil seine Offenstellung einnimmt. Die Strömung der in das Entlastungsventil eintretenden Reinigungsflüssigkeit unterliegt im Bereich des sich verkleinernden Strömungsquerschnittes einem Widerstand, so dass der im Einlassbereich des Durchgangskanals herrschende Druck ganz allmählich abgebaut wird.To ensure that the occurrence of a pressure peak in the pressure line, the desired pressure reduction takes a certain amount of time, the relief valve so gradually assumes its closed position, starting from its open position, in which the valve element reseals sealingly against the valve seat, it is advantageous if the flow cross-section of the Gangskanals in the region upstream of the at least one outlet channel is greater than the flow cross-section of the outlet channel. The exhaust passage thus forms a throttle element so that a substantial pressure is established upstream of the exhaust passage when the relief valve assumes its open position. The flow of the cleaning fluid entering the relief valve is subject to a resistance in the area of the decreasing flow cross-section, so that the pressure prevailing in the inlet region of the through-channel is very gradually reduced.
Von besonderem Vorteil ist es, wenn das Entlastungsventil einen einzigen Auslasskanal aufweist, denn dadurch können die Herstellungskosten des Entlastungsventils gering gehalten werden und mittels des einzigen Auslasskanals kann eine beträchtliche Drosselwirkung erzeugt werden.It is particularly advantageous if the relief valve has a single outlet channel, because this allows the manufacturing cost of the relief valve can be kept low and by means of the single outlet channel, a considerable throttle effect can be generated.
Günstig ist es, wenn das Ventilelement sowohl in der Offenstellung als auch in der Schließstellung des Entlastungsventiles den mindestens einen Auslasskanal zumindest teilweise freigibt. Eine derartige Ausgestaltung bewirkt, dass bei Abheben des Ventilelementes vom Ventilsitz sofort eine durchgängige Strömungsverbindung vom Ventileinlass über den Einlassbereich des Durchgangskanals und den Auslasskanal zum zweiten Ventilauslass sichergestellt ist, d. h. einströmende Flüssigkeit kann bereits bei einer geringfügigen Abhebebewegung des Ventilelementes vom Ventilsitz durch das Entlastungsventil hindurchströmen, es ist nicht erforderlich, dass das Ventilelement einen Mindestabstand zum Ventilsitz einnimmt, um die Strömungsverbindung zwischen Ventileinlass und zweiten Ventilauslass freizugeben. Bei einer bevorzugten Ausführungsform ist dem Ventilelement ein Anschlag zugeordnet, an dem das Ventilelement in der Offenstellung des Entlastungsventils anliegt. Der Anschlag bildet eine definierte Hubbegrenzung für das Ventilelement aus, so dass der gewünschte Hub des Ventilelementes durch die Lage des Anschlages konstruktiv vorgegeben werden kann.It is advantageous if the valve element at least partially releases the at least one outlet channel both in the open position and in the closed position of the relief valve. Such a configuration has the effect that, when the valve element is lifted off the valve seat, a continuous flow connection from the valve inlet via the inlet region of the passage channel and the outlet channel to the second valve outlet is ensured immediately, ie inflowing liquid can flow through the relief valve even with a slight lift-off movement of the valve element from the valve seat, it is not necessary that the valve member occupy a minimum distance to the valve seat, to release the flow connection between the valve inlet and the second valve outlet. In a preferred embodiment, the valve element is associated with a stop on which the valve element rests in the open position of the relief valve. The stop forms a defined stroke limitation for the valve element, so that the desired stroke of the valve element can be structurally predetermined by the position of the stop.
Es kann vorgesehen sein, dass der Anschlag von einer Verengung des Durchgangskanals gebildet ist. Der Durchgangskanal kann beispielsweise eine Stufe ausbilden, an der das Ventilelement in der Offenstellung des Entlastungsventils anliegen kann.It can be provided that the stop is formed by a constriction of the through-channel. The passageway may, for example, form a step at which the valve element may rest in the open position of the relief valve.
Alternativ kann vorgesehen sein, dass der Anschlag von einem im Durchgangskanal angeordneten Stützelement gebildet ist. Eine derartige Ausgestaltung hat den Vorteil, dass durch Wahl des Stützelementes die Lage des den Hub des Ventilelementes begrenzenden Anschlages vorgegeben werden kann. Das Stützelement steht bei einer bevorzugten Ausgestaltung radial nach innen von einer Innenwand des Durchgangskanals ab.Alternatively, it can be provided that the stop is formed by a support element arranged in the through-channel. Such a configuration has the advantage that by selecting the support element, the position of the stroke of the valve element limiting stop can be specified. The support member is in a preferred embodiment radially inwardly from an inner wall of the passageway.
Das Entlastungsventil weist bei einer bevorzugten Ausgestaltung ein erstes Gehäuseteil und ein zweites Gehäuseteil auf, die unter Zwischenlage eines Dichtringes miteinander verbindbar sind. Zum Verbinden der beiden Gehäuseteile kann eine lösbare oder auch eine unlösbare Verbindung, beispielsweise eine Rast- oder Schraubverbindung, zum Einsatz kommen.In a preferred embodiment, the relief valve has a first housing part and a second housing part, which can be connected to one another with the interposition of a sealing ring. For connecting the two housing parts, a detachable or even a permanent connection, for example a latching or screw connection, can be used.
Das erste Gehäuseteil umfasst bevorzugt den Ventileinlass, den Ventilsitz sowie den mindestens einen Auslasskanal und den zweiten Ventilauslass, und das zweite Gehäuseteil weist bevorzugt den ersten Ventilauslass auf. The first housing part preferably comprises the valve inlet, the valve seat and the at least one outlet channel and the second valve outlet, and the second housing part preferably has the first valve outlet.
Günstig ist es, wenn das zweite Gehäuseteil einen Einsatz umfasst, der unter Zwischenlage eines Dichtringes in das erste Gehäuseteil einsetzbar ist. Von Vorteil ist es, wenn der Einsatz außenseitig eine Ringnut trägt, in der der Dichtring angeordnet ist. Der Einsatz kann beispielsweise becherförmig ausgebildet sein und den dem Ventilsitz abgewandten Endbereich des Ventilelementes aufnehmen. In diesem Endbereich kann das Ventilelement eine Ringnut aufweisen, in der der das Ventilelement umgebende Dichtring angeordnet ist.It is advantageous if the second housing part comprises an insert which can be inserted with the interposition of a sealing ring in the first housing part. It is advantageous if the insert carries on the outside an annular groove in which the sealing ring is arranged. The insert may be, for example, cup-shaped and receive the end of the valve element facing away from the valve seat. In this end region, the valve element may have an annular groove in which the sealing ring surrounding the valve element is arranged.
Die Rückstellfeder ist vorzugsweise zwischen einem Bund des Ventilelementes und einer Stirnfläche des zweiten Gehäuseteiles eingespannt.The return spring is preferably clamped between a collar of the valve element and an end face of the second housing part.
Die nachfolgende Beschreibung zweier bevorzugter Ausführungsformen der Erfindung dient im Zusammenhang mit der Zeichnung der näheren Erläuterung. Es zeigen:The following description of two preferred embodiments of the invention is used in conjunction with the drawings for further explanation. Show it:
Figur 1: eine schematische Seitenansicht eines erfindungsgemäßen Hochdruckreinigungsgerätes;Figure 1: a schematic side view of a high-pressure cleaning device according to the invention;
Figur 2: eine vergrößerte Längsschnittansicht des Pumpenkopfes des Hochdruckreinigungsgerätes aus Figur 1;FIG. 2 is an enlarged longitudinal sectional view of the pump head of the high-pressure cleaning device from FIG. 1;
Figur 3: eine Längsschnittansicht einer ersten Ausführungsform eines Entlastungsventils des Hochdruckreinigungsgerätes aus Figur 1 und Figur 4: eine Längsschnittansicht einer zweiten Ausführungsform eines Entlastungsventils des Hochdruckreinigungsgerätes aus Figur 1.FIG. 3 shows a longitudinal sectional view of a first embodiment of a relief valve of the high-pressure cleaning device from FIG. 1 and FIG FIG. 4 shows a longitudinal sectional view of a second embodiment of a relief valve of the high-pressure cleaning device from FIG. 1.
In den Figuren 1 und 2 ist schematisch ein Hochdruckreinigungsgerät 10 dargestellt mit einem Gerätegehäuse 12, das eine Motorpumpeneinheit 14 aufnimmt. Letztere umfasst einen Elektromotor 15, ein sich daran anschließendes Getriebe 16 sowie eine über eine Taumelscheibe 17 angetriebene Kolbenpumpe 18 mit mehreren in axialer Richtung des Hochdruckreinigungsgerätes 10 reziprozierend verschiebbaren Kolben 19. Diese tauchen jeweils in einen Pumpraum 21 eines Pumpenkopfes 22 des Hochdruckreinigungsgerätes 10 ein. Die Pumpräume 21 sind jeweils über ein Saugventil 24 mit einer Saugleitung 25 und über ein Druckventil 27 mit einer Druckleitung 28 verbunden. Die Saugleitung 25 und die Druckleitung 28 sind hier allen Pumpräumen 21 des Pumpenkopfes 22 gemeinsam.FIGS. 1 and 2 schematically show a high-pressure cleaning device 10 with a device housing 12 which accommodates a motor pump unit 14. The latter includes an electric motor 15, an adjoining gear 16 and a driven via a swash plate 17 piston pump 18 with a plurality of reciprocating in the axial direction of the high-pressure cleaner 10 reciprocating piston 19. These dive into a pump chamber 21 of a pump head 22 of the high-pressure cleaner 10 a. The pump chambers 21 are each connected via a suction valve 24 to a suction line 25 and via a pressure valve 27 to a pressure line 28. The suction line 25 and the pressure line 28 are all pump chambers 21 of the pump head 22 together.
In die Druckleitung 28 ist ein federbelastetes Rückschlagventil 30 eingesetzt, an das sich in Strömungsrichtung ein den Strömungsquerschnitt der Druckleitung 28 verringernder Injektor 31 anschließt, der an seiner engsten Stelle über einen Ansaugkanal 32 mit einer Chemikalienansaugleitung 33 verbunden ist, die mittels eines Rückschlagventils 34 verschlossen ist.In the pressure line 28, a spring-loaded check valve 30 is used, in the flow direction of the flow cross-section of the pressure line 28 reducing injector 31 connects, which is connected at its narrowest point via a suction channel 32 with a Chemikalienansaugleitung 33, which is closed by a check valve 34 ,
Im Bereich zwischen dem in der Druckleitung 28 angeordneten Rückschlagventil 30 und dem Injektor 31 führt eine sich in Strömungsrichtung stufig erweiternde Rückströmleitung 36 von der Druckleitung 28 unmittelbar zur Saugleitung 25. In die Rückströmleitung 36 ist ein als selbständig handhabbare Patrone ausgestaltetes Entlastungsventil 38 eingesetzt, das in Umfangsrichtung von einem Dichtring 39 umgeben ist, der sich abdichtend an die Wandung der Rückströmleitung 36 anlegt.In the area between the arranged in the pressure line 28 check valve 30 and the injector 31 performs a gradually expanding in the flow direction Rückströmleitung 36 from the pressure line 28 directly to the suction line 25. In the return line 36 designed as a self-handle cartridge relief valve 38 is used, the circumferentially is surrounded by a sealing ring 39 which applies sealingly against the wall of the return line 36.
Das Entlastungsventil 38 ist in Figur 3 vergrößert dargestellt. Es umfasst ein zweiteiliges Gehäuse mit einem ersten Gehäuseteil 41, das in einer Umfangs- nut 42 den Dichtring 39 trägt und abgedichtet in die Rückströmleitung 36 einsetzbar ist. Außerdem umfasst das Entlastungsventil 38 ein zweites, becherförmiges Gehäuseteil 44 mit einem zylinderförmigen Mantel 45 und einer Bodenwand 46. Das zweite Gehäuseteil 44 ist mit dem ersten Gehäuseteil 41 verrastet. Hierzu weist das erste Gehäuseteil 41 an seinem der Umfangsnut 42 abgewandten Ende eine Ringnut 48 auf, in die eine nach innen vorspringende Ringschulter 49 des zweiten Gehäuseteils 44 elastisch eingreifen kann, wenn das zweite Gehäuseteil 44 in axialer Richtung auf das erste Gehäuseteil 41 aufgeschoben wird.The relief valve 38 is shown enlarged in FIG. It comprises a two-part housing with a first housing part 41 which carries the sealing ring 39 in a circumferential groove 42 and can be inserted sealed into the return flow line 36. In addition, the relief valve 38 comprises a second, cup-shaped housing part 44 with a cylindrical jacket 45 and a bottom wall 46. The second housing part 44 is latched to the first housing part 41. For this purpose, the first housing part 41 at its circumferential groove 42 remote from the end an annular groove 48 into which an inwardly projecting annular shoulder 49 of the second housing part 44 can engage elastically when the second housing part 44 is pushed in the axial direction on the first housing part 41.
Die beiden Gehäuseteile 41 und 44 definieren einen Durchgangskanal 50, der ausgehend von einem stirnseitigen Ventileinlass 52 einen ersten Kanalabschnitt 53 ausbildet, der über eine kugelige Erweiterung 54 in einen zweiten Kanalabschnitt 56 übergeht. Die Erweiterung 54 bildet einen Ventilsitz 58 aus für den Schließkörper 60 eines in Längsrichtung des Durchgangskanals 50 beweglich im Durchgangskanal 50 gehaltenen Ventilelements 61. Der Schließkörper 60 ist in Form einer Kugelkalotte ausgestaltet und liegt in der in Figur 3 dargestellten Schließstellung des Entlastungsventils 38 dichtend am Ventilsitz 58 an. In axialer Richtung schließt sich an den Schließkörper 60 ein Druckkörper 63 des Ventilelementes 61 an. Der Druckkörper 63 ist in Form eines Kolbens ausgebildet und trägt außenseitig eine Umfangsnut 64, in der ein das Ventilelement 61 in Umfangsrichtung umgebender Dichtring 66 angeordnet ist. Der Dichtring 66 liegt an der Wandung des Durchgangskanals 50 im Bereich von dessen zweiten Kanalabschnitt 56 an.The two housing parts 41 and 44 define a through-channel 50 which, starting from a front-side valve inlet 52, forms a first channel section 53, which merges via a spherical extension 54 into a second channel section 56. The extension 54 forms a valve seat 58 for the closing body 60 of a longitudinally of the passage channel 50 movably held in the passage 50 valve member 61. The closing body 60 is configured in the form of a spherical cap and is in the closed position shown in Figure 3 of the relief valve 38 sealingly against the valve seat 58 on. In the axial direction, a pressure body 63 of the valve element 61 connects to the closing body 60. The pressure body 63 is designed in the form of a piston and carries on the outside a circumferential groove 64, in which a sealing element 66 surrounding the valve element 61 in the circumferential direction is arranged. The sealing ring 66 abuts against the wall of the through-channel 50 in the region of its second channel section 56.
An den zweiten Kanalabschnitt 56 schließt sich in axialer Richtung über eine konische Erweiterung 68 ein dritter Kanalabschnitt 69 an, der über eine stufige Erweiterung 71 in einen vierten Kanalabschnitt 72 übergeht. Der vierte Kanalabschnitt 72 wird vom Mantel 45 des zweiten Gehäuseteiles 44 definiert. Er weist in axialer Richtung verlaufende und radial vom Mantel 45 nach innen vorspringende Längsrippen 74 auf, die sich bis zu die Bodenwand 46 durchgreifenden ersten Ventilauslässen 75 erstrecken.Connected to the second channel section 56 in the axial direction via a conical extension 68 is a third channel section 69, which merges via a stepped extension 71 into a fourth channel section 72. The fourth channel section 72 is defined by the jacket 45 of the second housing part 44. It has in the axial direction extending and radially from the jacket 45 inwardly projecting longitudinal ribs 74, which extend to the bottom wall 46 by cross-first valve outlets 75.
Der vierte Kanalabschnitt 72 nimmt eine als Schraubenfeder ausgestaltete Rückstellfeder 77 auf, die sich einerseits an der Bodenwand 46 des zweiten Gehäuseteils 44 und andererseits an der der Bodenwand 46 zugewandten Unterseite 78 des Druckkörpers 63 abstützt. Mittels der Rückstellfeder 77 werden der Druckkörper 63 und der Schließkörper 60 mit einer Federkraft in Richtung des Ventilsitzes 58 beaufschlagt, so dass der Schließkörper 60 in der Schließstellung des Entlastungsventils 38 am Ventilsitz 58 dicht anliegt, wie dies in Figur 3 dargestellt ist.The fourth channel section 72 accommodates a return spring 77 configured as a helical spring, which is supported on the bottom wall 46 of the second housing part 44 on the one hand and on the underside 78 of the pressure body 63 facing the bottom wall 46 on the other hand. By means of the return spring 77, the pressure body 63 and the closing body 60 are acted upon by a spring force in the direction of the valve seat 58, so that the closing body 60 in the closed position of the relief valve 38 against the valve seat 58 tightly, as shown in Figure 3.
Die obere, dem Druckkörper 63 zugewandte Stirnseite 80 der Längsrippen 74 bildet einen Anschlag aus für den Druckkörper 63 des Ventilelementes 61, wenn dieser in der Offenstellung des Entlastungsventils 38 vom Ventilsitz 58 abhebt. Dies wird nachstehend noch näher erläutert.The upper, the pressure body 63 facing end face 80 of the longitudinal ribs 74 forms a stop for the pressure body 63 of the valve member 61 when it lifts in the open position of the relief valve 38 from the valve seat 58. This will be explained in more detail below.
Das erste Gehäuseteil 41 weist im Abstand vom Ventilsitz 58 im zweiten Kanalabschnitt 56 des Durchgangskanals 50 einen radial verlaufenden Auslass- kanal 88 auf, dessen radial außenliegender Endbereich einen zweiten Ven- tilauslass 89 des Entlastungsventils 38 ausbildet.The first housing part 41 has, at a distance from the valve seat 58 in the second passage section 56 of the passage channel 50, a radially extending exhaust port. channel 88, whose radially outer end region forms a second valve outlet 89 of the relief valve 38.
Der das Ventilelement 61 in Umfangsrichtung umgebende Dichtring 66 unterteilt den Durchgangskanal 50 in einen Einlassbereich 91 und einen Auslassbereich 92. Der Einlassbereich 91 wird vom ersten Kanalabschnitt 53, der kugeligen Erweiterung 54 und dem den Schließkörper 60 umgebenden Bereich des zweiten Kanalabschnittes 56 gebildet. Der Auslassbereich 92 wird von dem sich an den Schließkörper 60 anschließenden Bereich des zweiten Kanalabschnitts 56, der konischen Erweiterung 68, dem dritten Kanalabschnitt 69 sowie der stufigen Erweiterung 71 und dem vierten Kanalabschnitt 72 gebildet.The sealing ring 66 surrounding the valve element 61 in the circumferential direction divides the through-passage 50 into an inlet region 91 and an outlet region 92. The inlet region 91 is formed by the first channel section 53, the spherical extension 54 and the region of the second channel section 56 surrounding the closing body 60. The outlet region 92 is formed by the area adjoining the closing body 60 of the second channel section 56, the conical extension 68, the third channel section 69 and the stepped extension 71 and the fourth channel section 72.
Während des normalen Betriebes des Hochdruckreinigungsgerätes 10, d. h. bei der Ausgabe von unter Druck stehender Reinigungsflüssigkeit über die Druckleitung 28 an einen an diese anschließbaren Hochdruckschlauch (in der Zeichnung nicht dargestellt), wird das Ventilelement 61 von der Rückstellfeder 77 gegen den Ventilsitz 58 gedrückt, so dass das Entlastungsventil 38 seine Schließstellung einnimmt, in der die Strömungsverbindung vom Ventileinlass 52 über den Einlassbereich 91 des Durchgangskanals 50 und den Auslasskanal 88 zum zweiten Ventilauslass 89 unterbrochen ist.During normal operation of the high pressure cleaner 10, d. H. in the issue of pressurized cleaning fluid via the pressure line 28 to a high pressure hose connectable to this (not shown in the drawing), the valve element 61 is pressed by the return spring 77 against the valve seat 58, so that the relief valve 38 assumes its closed position, in the flow connection from the valve inlet 52 via the inlet region 91 of the through-channel 50 and the outlet channel 88 to the second valve outlet 89 is interrupted.
Bei Überschreiten eines bestimmten Druckwertes der Reinigungsflüssigkeit, wie dies beispielsweise beim Abschalten des Hochdruckreinigungsgerätes 10 auftreten kann, wird das Ventilelement 61 entgegen der Federkraft der Rückstellfeder 77 vom Ventilsitz 58 abgehoben und in die dem Ventilsitz 58 abgewandte Richtung nach unten verschoben, bis der Druckkörper 63 mit seiner Unterseite 78 an der freien Stirnseite 80 der Längsrippen 74 anliegt. Die Längsrippen 74 begrenzen somit die Hubbewegung des Ventilelementes 61. Durch das Abheben des Ventilelementes 61 vom Ventilsitz 58 wird die Strömungsverbindung zwischen dem Ventileinlass 52 und dem zweiten Ventilaus- lass 89 freigegeben, wobei sich innerhalb des Einlassbereiches 91 des Durchgangskanals 50 ein beträchtlicher Druck einstellt, wohingegen im Auslassbereich 92 des Durchgangskanals 50, der mittels des Dichtrings 66 vom Einlassbereich 91 getrennt ist, ein beträchtlich geringerer Druck vorliegt, nämlich der in der Saugleitung 35 herrschende Druck. Somit wirkt in der Offenstellung des Entlastungsventils 38 auf das Ventilelement 61 eine Druckdifferenz ein, die zur Folge hat, dass das Ventilelement 61 mit einer axial entgegen der Wirkung der Rückstellfeder 77 wirkenden Kraft beaufschlagt wird, die das Ventilelement 61 so lange zuverlässig im Abstand vom Ventilsitz 58 hält, bis sich der Druck der Reinigungsflϋssigkeit im Einlassbereich 91 so weit abgesenkt hat, dass die Kraft der Rückstellfeder 77 ausreicht, um das Ventilelement zum Ventilsitz 58 zurückzuführen. Die in der Offenstellung des Entlastungsventils 38 auf das Ventilelement 61 einwirkende Druckdifferenz verringert das Auftreten von Schwingungsbewegungen des Ventilelementes 61.When exceeding a certain pressure value of the cleaning liquid, as may occur, for example, when switching off the high-pressure cleaner 10, the valve member 61 is lifted against the spring force of the return spring 77 from the valve seat 58 and moved in the valve seat 58 facing away from the direction down to the pressure body 63 with its bottom 78 abuts against the free end face 80 of the longitudinal ribs 74. The The lifting of the valve element 61 from the valve seat 58 releases the flow connection between the valve inlet 52 and the second valve outlet 89, whereby a considerable pressure is established within the inlet region 91 of the through-channel 50, whereas In the outlet region 92 of the through-channel 50, which is separated from the inlet region 91 by means of the sealing ring 66, there is a considerably lower pressure, namely the pressure prevailing in the suction line 35. Thus, in the open position of the relief valve 38 acts on the valve element 61, a pressure difference, which has the consequence that the valve element 61 is acted upon by an axially against the action of the return spring 77 acting force, the valve member 61 reliably as long as the distance from the valve seat 58 holds until the pressure of the cleaning liquid in the inlet region 91 has lowered so far that the force of the return spring 77 is sufficient to return the valve element to the valve seat 58. The pressure difference acting on the valve element 61 in the open position of the relief valve 38 reduces the occurrence of oscillatory movements of the valve element 61.
In Figur 4 ist eine zweite Ausführungsform eines Entlastungsventils dargestellt, das alternativ zum Entlastungsventil 38 beim Hochdruckreinigungsgerät 10 zum Einsatz kommen kann. Es ist insgesamt mit dem Bezugszeichen 98 belegt. Das Entlastungsventil 98 weist ein erstes Gehäuseteil 101 und ein zweites Gehäuseteil 102 auf. Außenseitig trägt das erste Gehäuseteil 101 eine Umfangsnut 104, die einen Dichtring 105 aufnimmt, der sich beim Einsetzen des als selbständig handhabbare Patrone ausgestalteten Entlastungsventils 98 in die Rückströmleitung 36 abdichtend an die Wandung der Rückströmleitung 36 anlegt. 4 shows a second embodiment of a relief valve is shown, which can be used as an alternative to the relief valve 38 in the high-pressure cleaner 10. It is altogether occupied by the reference numeral 98. The relief valve 98 has a first housing part 101 and a second housing part 102. On the outside, the first housing part 101 carries a circumferential groove 104, which receives a sealing ring 105 which abuts sealingly against the wall of the return flow line 36 in the return flow line 36 when the relief valve 98 designed as a self-contained cartridge is inserted.
Die Gehäuseteile 101 und 102 sind miteinander verrastet. Alternativ könnte beispielsweise auch eine Schraubverbindung zum lösbaren Verbinden der beiden Gehäuseteile 101, 102 zum Einsatz kommen.The housing parts 101 and 102 are locked together. Alternatively, for example, a screw connection for detachably connecting the two housing parts 101, 102 could be used.
Die beiden Gehäuseteile 101 und 102 definieren einen Durchgangskanal 107. Dieser geht aus von einem stirnseitigen Ventileinlass 109 des ersten Gehäuseteiles 101 und erstreckt sich mit einem ersten zylindrischen Kanalabschnitt 111 bis zu einer ersten konischen Erweiterung 112, an die sich ein zweiter zylindrischer Kanalabschnitt 113 anschließt, der über eine zweite konische Erweiterung 114 in einen dritten zylindrischen Kanalabschnitt 115 übergeht. Der dritte zylindrische Kanalabschnitt 115 ist von einem Mantel 117 des ersten Gehäuseteils 101 umgeben. In den Mantel 117 taucht das zweite Gehäuseteil 102 mit einem becherförmigen Einsatz 119 ein, der einen vierten zylindrischen Kanalabschnitt 120 des Durchgangskanals 107 definiert.The two housing parts 101 and 102 define a passage 107. This proceeds from a front-side valve inlet 109 of the first housing part 101 and extends with a first cylindrical channel portion 111 to a first conical extension 112, which is followed by a second cylindrical channel portion 113, which merges via a second conical extension 114 in a third cylindrical channel section 115. The third cylindrical channel section 115 is surrounded by a jacket 117 of the first housing part 101. In the shell 117, the second housing part 102 dives with a cup-shaped insert 119, which defines a fourth cylindrical channel portion 120 of the passage channel 107.
Der Einsatz 119 ist einstückig mit einer Bodenwand 122 des zweiten Gehäuseteils 102 verbunden, die das freie Ende des Mantels 117 des ersten Gehäuseteils 101 verschließt. Auf der dem Einsatz 119 abgewandten Seite schließt sich an die Bodenwand 122 eine zylindrische Verlängerung 123 an, die ebenso wie die Bodenwand 122 von einer axial verlaufenden Durchgangsbohrung 124 durchgriffen ist. Die Durchgangsbohrung 124 bildet einen fünften zylindrischen Kanalabschnitt 125 des Durchgangskanals 107 aus, wobei im Übergangsbereich zwischen dem vierten Kanalabschnitt 120 und dem fünften Kanalabschnitt 125 eine stufige Verengung 126 angeordnet ist. Der becherförmige Einsatz 119 trägt auf seiner Außenseite eine Ringnut 129, in der ein Dichtring 130 angeordnet ist, der eine flüssigkeitsdichte Verbindung zwischen dem ersten Gehäuseteil 101 und dem zweiten Gehäuseteil 102 sicherstellt.The insert 119 is integrally connected to a bottom wall 122 of the second housing part 102, which closes the free end of the shell 117 of the first housing part 101. On the side facing away from the insert 119 connects to the bottom wall 122, a cylindrical extension 123, which is like the bottom wall 122 penetrated by an axially extending through hole 124. The through-bore 124 forms a fifth cylindrical passage section 125 of the through-passage 107, a stepped narrowing 126 being arranged in the transitional area between the fourth passage section 120 and the fifth passage section 125. The cup-shaped insert 119 carries on its outer side an annular groove 129, in which a sealing ring 130 is arranged, which ensures a liquid-tight connection between the first housing part 101 and the second housing part 102.
Innerhalb des Durchgangskanals 107 ist ein Ventilelement 132 beweglich gelagert mit einem in Form einer Kugelkalotte ausgestalteten Schließkörper 133 und einem sich an diesen axial anschließenden Druckkörper 134. Der Schließkörper 133 liegt in der in Figur 4 dargestellten Schließstellung des Entlastungsventils 98 an einem von der ersten konischen Erweiterung 112 ausgebildeten Ventilsitz 136 dicht an. Der Druckkörper 134 erstreckt sich vom Schließkörper 133 bis in den Bereich des vierten Kanalabschnittes 120, wo er außenseitig eine Ringnut 138 trägt, in der ein das Ventilelement 132 in Um- fangsrichtung umgebender Dichtring 139 angeordnet ist. Der Innendurchmesser des Dichtringes ist größer gewählt als der Durchmesser des Bodens der Ringnut 138. Dies hat zur Folge, dass der Dichtring 139 einen Abstand zum Boden der Ringnut 138 einnimmt, wie dies in Figur 4 dargestellt ist. Außenseitig liegt der Dichtring 139 an der Wandung des vierten Kanalabschnittes 120 dicht an.Within the passage 107, a valve member 132 is movably mounted with a designed in the form of a spherical cap closing body 133 and an axially adjoining this pressure body 134. The closing body 133 is in the closed position shown in Figure 4 of the relief valve 98 at one of the first conical extension 112 formed valve seat 136 tightly. The pressure body 134 extends from the closing body 133 into the region of the fourth channel section 120, where it bears on the outside an annular groove 138 in which a sealing ring 139 surrounding the valve element 132 in the circumferential direction is arranged. The inner diameter of the sealing ring is selected larger than the diameter of the bottom of the annular groove 138. This has the consequence that the sealing ring 139 is at a distance from the bottom of the annular groove 138, as shown in Figure 4. On the outside, the sealing ring 139 is tight against the wall of the fourth channel section 120.
Im Abstand zum Schließkörper 133 weist der Druckkörper 134 unterhalb der Längsachse 141 eines radial verlaufenden Auslasskanals 142 einen Bund 144 auf. Eine den Druckkörper 134 im dritten Kanalabschnitt 115 in Umfangsrich- tung umgebende, als Schraubenfeder ausgebildete Rückstellfeder 146 stützt sich einerseits an der dem Ventilsitz 136 zugewandten freien Stirnseite 148 des becherförmigen Einsatzes 119 und andererseits an der dem Ventilsitz 136 abgewandten Unterseite 149 des Bundes 144 ab. Mittels der Rückstellfeder 146 wird das Ventilelement 132 mit einer Federkraft in Richtung auf den Ventilsitz 136 beaufschlagt.At a distance from the closing body 133, the pressure body 134 has a collar 144 below the longitudinal axis 141 of a radially extending outlet channel 142. A restoring spring 146, which surrounds the pressure body 134 in the third channel section 115 in the circumferential direction and is designed as a helical spring, is braced, on the one hand, on the free end face 148 of the cup-shaped insert 119 facing the valve seat 136 and on the other side on the underside 149 of the collar 144 facing away from the valve seat 136. By means of the return spring 146, the valve element 132 is acted upon by a spring force in the direction of the valve seat 136.
Der die Bodenwand 122 und die axiale Verlängerung 123 durchgreifende fünfte Kanalabschnitt 125 bildet mit seinem freien Endbereich einen ersten Ventilauslass 151, und der vom Durchgangskanal 107 ausgehende Auslasskanal 142 bildet mit seinem radial außenliegenden Endbereich einen zweiten Ventilauslass 152. Der Durchgangskanal 107 wird von dem das Ventilelement 132 in Umfangsrichtung umgebenden Dichtring 139 in einen Einlassbereich 154 und einen Auslassbereich 155 unterteilt, die mittels des Dichtringes 139 flüssigkeitsdicht voneinander getrennt sind. Der Einlassbereich 154 wird vom ersten Kanalabschnitt 111, der ersten konischen Erweiterung 112, dem zweiten Kanalabschnitt 113, der zweiten konischen Erweiterung 114, dem dritten Kanalabschnitt 115 sowie dem der freien Stirnseite 148 benachbarten Teil des vierten Kanalabschnittes 120 gebildet. Der Auslassbereich 155 des Durchgangskanals 107 wird von dem der stufigen Verengung 126 benachbarten Teil des vierten Kanalabschnittes 120 sowie dem fünften Kanalabschnitt 125 gebildet.The fifth channel section 125 extending through the bottom wall 122 and the axial extension 123 forms with its free end region a first valve outlet 151, and the outlet channel 142 emanating from the through-channel 107 forms with its radially outer end region a second valve outlet 152. The passage 107 becomes the valve element 132 circumferentially surrounding sealing ring 139 into an inlet portion 154 and an outlet portion 155, which are separated by the sealing ring 139 liquid-tight from each other. The inlet region 154 is formed by the first channel section 111, the first conical extension 112, the second channel section 113, the second conical extension 114, the third channel section 115 and the part of the fourth channel section 120 which is adjacent to the free end side 148. The outlet region 155 of the through-channel 107 is formed by the portion of the fourth channel section 120 adjacent to the stepped constriction 126 and the fifth channel section 125.
Während des Normalbetriebes des Hochdruckreinigungsgerätes nimmt das Entlastungsventil 98 seine Schließstellung ein, in der das Ventilelement 132 mit dem Schließkörper 133 dicht am Ventilsitz 136 anliegt. Bei Überschreiten eines bestimmten Druckwertes der Reinigungsflüssigkeit innerhalb der Druckleitung 28 wird das Ventilelement 132 entgegen der Kraft der Rückstellfeder 146 vom Ventilsitz 136 abgehoben, bis der Druckkörper 134 mit seinem dem Schließkörper 133 abgewandten Ende an der stufigen Verengung 126 anliegt. Die stufige Verengung 126 bildet somit einen Anschlag zur Begrenzung des Hubes des Ventilelementes 132 aus. Durch das Abheben des Ventilelementes 132 vom Ventilsitz 136 wird eine Strömungsverbindung vom Ventileinlass 107 zum zweiten Ventilauslass 152 freigegeben, so dass überschüssige Flüssigkeit aus der Druckleitung 28 über die Rückströmleitung 36 zur Saugleitung 25 entweichen kann. Hierbei stellt sich im Einlassbereich 154 des Durchgangskanals 107 ein beträchtlicher Druck ein, wohingegen im Auslassbereich 155 ein beträchtlich geringerer Druck vorliegt, nämlich der in der Saugleitung 25 herrschende Druck. Dies führt dazu, dass auf das Ventilelement 132 ein Differenzdruck wirkt, der eine dem Ventilsitz 136 abgewandte Kraftbeaufschlagung zur Folge hat. Aufgrund dieser Kraftbeaufschlagung behält das Ventilelement 132 so lange seine vom Ventilsitz 136 beabstandete Stellung, bis sich der Überdruck in der Druckleitung 28 abgebaut hat. Der Druckabbau erfolgt hierbei allmählich, da der Strömungsquerschnitt des Auslasskanals 142 geringer gewählt ist als der Strömungsquerschnitt des Durchgangskanals stromaufwärts des Auslasskanals 142. Letzterer bildet ein Drosselelement für die das Entlastungsventil 98 durchströmende Reinigungsflüssigkeit aus, das sicherstellt, dass sich im Einlassbereich 154 des Durchgangskanals 107 ein beachtlicher Druck aufbaut, wenn das Entlastungsventil 98 seine Offenstellung einnimmt. During normal operation of the high-pressure cleaning device, the relief valve 98 assumes its closed position, in which the valve element 132 bears tightly against the valve seat 136 with the closing body 133. When a certain pressure value of the cleaning fluid within the pressure line 28 is exceeded, the valve element 132 is lifted against the force of the return spring 146 from the valve seat 136 until the pressure element 134 abuts with its end facing away from the closing body 133 at the stepped constriction 126. The stepped constriction 126 thus forms a stop to limit the Strokes of the valve element 132 from. By lifting the valve element 132 from the valve seat 136, a flow connection from the valve inlet 107 to the second valve outlet 152 is released so that excess liquid can escape from the pressure line 28 via the return line 36 to the suction line 25. Here, a considerable pressure arises in the inlet region 154 of the through-channel 107, whereas in the outlet region 155 a considerably lower pressure is present, namely the pressure prevailing in the suction line 25. As a result, a differential pressure acts on the valve element 132, which results in a force application facing away from the valve seat 136. Due to this application of force, the valve element 132 retains its position spaced from the valve seat 136 until the overpressure in the pressure line 28 has decreased. In this case, the pressure reduction takes place gradually, since the flow cross-section of the outlet channel 142 is selected smaller than the flow cross-section of the passage channel upstream of the outlet channel 142. The latter forms a throttle element for the cleaning fluid flowing through the relief valve 98, which ensures that in the inlet region 154 of the through-channel 107 a builds considerable pressure when the relief valve 98 assumes its open position.

Claims

P AT E N T A N S P R Ü C H E P AT TESTS
1. Hochdruckreinigungsgerät mit einer Hochdruckpumpe, die mindestens einen Pumpraum aufweist, der mit einer Saugleitung und einer Druckleitung verbunden ist, wobei die Druckleitung über eine Rückströmleitung mit der Saugleitung in Strömungsverbindung steht und in der Rückströmleitung ein Entlastungsventil angeordnet ist, wobei des Entlastungsventil einen Durchgangskanal umfasst, der sich von einem Ventil- einlass zu einem ersten Ventilauslass erstreckt und der einen Ventilsitz ausbildet, wobei stromabwärts des Ventilsitzes vom Durchgangskanal mindestens ein Auslasskanal abzweigt, der in einen zweiten Ventilauslass einmündet, und wobei im Durchgangskanal ein Ventilelement beweglich gehalten ist, das mittels einer Rückstellfeder an den Ventilsitz dichtend anlegbar ist, dadurch gekennzeichnet, dass das Ventilelement (61; 132) in der dem Ventilsitz (58; 136) abgewandten Richtung im Abstand zu dem mindestens einen Auslasskanal (88; 142) von einem Dichtring (66; 139) umgeben ist, der einen dem Ventileinlass (52; 109) benachbarten Einlassbereich (91, 154) des Durchgangskanals (50; 107) von einem dem ersten Ventilauslass (75; 151) benachbarten Auslassbereich (92, 155) des Durchgangskanals (50; 107) abdichtet.A high-pressure cleaning device having a high-pressure pump, which has at least one pump chamber which is connected to a suction line and a pressure line, wherein the pressure line via a return line to the suction line in flow communication and in the return line a relief valve is arranged, wherein the relief valve comprises a passage extending from a valve inlet to a first valve outlet and forming a valve seat, wherein downstream of the valve seat from the passageway at least one outlet channel branches off, which opens into a second valve outlet, and wherein in the passageway a valve element is movably held by means of a The return spring is sealingly engageable with the valve seat, characterized in that the valve element (61, 132) is spaced apart from the at least one outlet channel (88, 142) by a sealing ring (66, 139) in the direction away from the valve seat (58; 136). is surrounded, d he a the valve inlet (52; 109) adjacent the inlet region (91, 154) of the passageway (50; 107) from a first valve outlet (75; 151) adjacent the outlet region (92, 155) of the passageway (50; 107) seals.
2. Hochdruckreinigungsgerät nach Anspruch 1, dadurch gekennzeichnet, dass der Dichtring (66; 139) in einer Umfangsnut (64; 138) des Ventilelements (61; 132) angeordnet ist. 2. High-pressure cleaning device according to claim 1, characterized in that the sealing ring (66; 139) in a circumferential groove (64; 138) of the valve element (61; 132) is arranged.
3. Hochdruckreinigungsgerät nach Anspruch 2, dadurch gekennzeichnet, dass der Innendurchmesser des Dichtringes (66; 139) größer ist als der Durchmesser des Bodens der Umfangsnut (64; 138).3. High-pressure cleaning device according to claim 2, characterized in that the inner diameter of the sealing ring (66; 139) is greater than the diameter of the bottom of the circumferential groove (64; 138).
4. Hochdruckreinigungsgerät nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, dass das Ventilelement (61; 132) einen Schließkörper (60; 133) aufweist, der an den Ventilsitz (58; 136) dichtend anlegbar ist, sowie einen Druckkörper (63; 134), der im Abstand zum Schließkörper (60; 133) vom Dichtring (66; 139) umgeben ist.4. High-pressure cleaning device according to claim 1, 2 or 3, characterized in that the valve element (61; 132) has a closing body (60; 133), which is sealingly engageable with the valve seat (58; 136), and a pressure body (63; 134) which is surrounded by the sealing ring (66; 139) at a distance from the closing body (60; 133).
5. Hochdruckreinigungsgerät nach Anspruch 4, dadurch gekennzeichnet, dass der Durchgangskanal (50; 107) einen Führungsabschnitt (56; 120) umfasst, an dessen Innenwand der Druckkörper (63; 134) unter Zwischenlage des Dichtringes (66; 139) verschiebbar gelagert ist.5. High-pressure cleaning device according to claim 4, characterized in that the passage channel (50; 107) comprises a guide section (56; 120) on the inner wall of the pressure body (63; 134) with the interposition of the sealing ring (66; 139) is displaceably mounted.
6. Hochdruckreinigungsgerät nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass der Strömungsquerschnitt des Durchgangskanals (50; 107) im Bereich stromaufwärts des mindestens einen Auslasskanals (88; 142) größer ist als der Strömungsquerschnitt des Auslasskanals (88; 142).6. High-pressure cleaning device according to one of the preceding claims, characterized in that the flow cross-section of the passage channel (50; 107) in the region upstream of the at least one outlet channel (88; 142) is greater than the flow cross-section of the outlet channel (88; 142).
7. Hochdruckreinigungsgerät nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass das Entlastungsventil (38; 98) einen einzigen Auslasskanal (88; 142) aufweist.7. High-pressure cleaning device according to one of the preceding claims, characterized in that the relief valve (38, 98) has a single outlet channel (88, 142).
8. Hochdruckreinigungsgerät nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass das Ventilelement (61; 132) sowohl in der Offenstelllung als auch in der Schließstellung des Entlastungsventils (38; 98) den mindestens einen Auslasskanal (88; 142) zumindest teilweise freigibt.8. High-pressure cleaning device according to one of the preceding claims, characterized in that the valve element (61, 132) both in the Open position as well as in the closed position of the relief valve (38, 98) at least partially releases the at least one outlet channel (88, 142).
9. Hochdruckreinigungsgerät nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass dem Ventilelement (61; 132) ein Anschlag (80; 126) zugeordnet ist, an dem das Ventilelement (61; 132) in der Offenstellung des Entlastungsventils (38; 98) anliegt.9. High-pressure cleaning device according to one of the preceding claims, characterized in that the valve element (61; 132) is assigned a stop (80; 126) against which the valve element (61; 132) rests in the open position of the relief valve (38; ,
10. Hochdruckreinigungsgerät nach Anspruch 9, dadurch gekennzeichnet, dass der Anschlag von einer Verengung (126) des Durchgangskanals (107) gebildet ist.10. High-pressure cleaning device according to claim 9, characterized in that the stop of a constriction (126) of the through-channel (107) is formed.
11. Hochdruckreinigungsgerät nach Anspruch 9, dadurch gekennzeichnet, dass der Anschlag (80) von einem in den Durchgangskanal (50) ragenden Stützelement (74) gebildet ist.11. High-pressure cleaning device according to claim 9, characterized in that the stop (80) by a in the passageway (50) projecting support member (74) is formed.
12. Hochdruckreinigungsgerät nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass das Entlastungsventil (98) ein erstes Gehäuseteil (101) und ein zweites Gehäuseteil (102) aufweist, die unter Zwischenlage eines Dichtringes (130) mit einander verbindbar sind. 12. High-pressure cleaning device according to one of the preceding claims, characterized in that the relief valve (98) has a first housing part (101) and a second housing part (102), which are connected with the interposition of a sealing ring (130) with each other.
EP08735129A 2007-04-11 2008-04-10 High-pressure cleaning device Active EP2131970B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007017970A DE102007017970A1 (en) 2007-04-11 2007-04-11 High-pressure cleaner
PCT/EP2008/002818 WO2008125267A1 (en) 2007-04-11 2008-04-10 High-pressure cleaning device

Publications (2)

Publication Number Publication Date
EP2131970A1 true EP2131970A1 (en) 2009-12-16
EP2131970B1 EP2131970B1 (en) 2011-01-19

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ID=39598405

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08735129A Active EP2131970B1 (en) 2007-04-11 2008-04-10 High-pressure cleaning device

Country Status (7)

Country Link
US (1) US8790092B2 (en)
EP (1) EP2131970B1 (en)
CN (1) CN101641165B (en)
AT (1) ATE495828T1 (en)
DE (2) DE102007017970A1 (en)
DK (1) DK2131970T3 (en)
WO (1) WO2008125267A1 (en)

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DE102009049094A1 (en) * 2009-10-01 2011-04-07 Alfred Kärcher Gmbh & Co. Kg Pump for a high-pressure cleaning device
CN102953974B (en) * 2011-08-31 2016-05-25 宁波蓝达实业有限公司 For the self priming pump of jetting machine
EP2805055B1 (en) * 2012-01-20 2016-05-25 Alfred Kärcher GmbH & Co. KG Piston pump for a high-pressure cleaning device
DE102014208891B3 (en) * 2014-05-12 2015-09-24 Continental Automotive Gmbh Pressure relief valve and component for a fuel injection system and method for producing a pressure relief valve
DE102022100388A1 (en) 2022-01-10 2023-07-13 Alfred Kärcher SE & Co. KG Motor pump unit, in particular for a high-pressure cleaning device

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Also Published As

Publication number Publication date
US20100059603A1 (en) 2010-03-11
CN101641165A (en) 2010-02-03
EP2131970B1 (en) 2011-01-19
ATE495828T1 (en) 2011-02-15
DE502008002391D1 (en) 2011-03-03
US8790092B2 (en) 2014-07-29
DK2131970T3 (en) 2011-05-16
WO2008125267A1 (en) 2008-10-23
DE102007017970A1 (en) 2008-10-16
WO2008125267A8 (en) 2008-12-18
CN101641165B (en) 2012-11-07

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