EP2131970B1 - High-pressure cleaning device - Google Patents

Abstract

A high-pressure cleaning appliance with a high-pressure pump is provided. The pump has at least one pump chamber connected to a suction line and a pressure line. The pressure line is in flow connection with the suction line via a return flow line. A relief valve with a through-channel extending from a valve inlet to a first valve outlet is arranged in the return flow line. A valve element which in a closed position bears against a valve seat is held for movement in the through-channel. At least one outlet channel, which opens into a second valve outlet, branches off from the through-channel. The valve element is surrounded by a sealing ring which seals off an inlet area of the through-channel adjacent to the valve inlet from an outlet area of the through-channel adjacent to the first valve outlet.

Description

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, wherein 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 from the DE 297 12 659 U1 known. 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.

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 aid of a dipping into the pump chamber and reciprocally displaceable 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 element 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.

Out EP 0 631 054 A and from US 5,409,032 A a high-pressure cleaning device is known in which a relief valve is arranged in a pressure line from which an outlet channel branches, leading to a return line. The relief valve comprises a valve housing having a passageway in which a two-part valve piston is slidably supported between a front and a rear end position. By means of an upstream the outlet channel arranged first sealing ring and a downstream of the outlet channel arranged second sealing ring, the valve piston in the valve housing is guided in a flow-tight manner. The valve piston comprises a longitudinal channel through which the liquid can flow from the valve inlet to the valve outlet. From the longitudinal channel branches off a discharge channel, which is positioned in the rear end position of the valve piston between the two sealing rings and a flow connection between the longitudinal channel and the outlet channel releases. The high-pressure cleaning device can thereby be operated in the circuit. If the valve piston assumes its front end position, the discharge channel is arranged downstream of the second sealing ring and the flow connection between the longitudinal channel and the outlet channel is interrupted.

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.

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.

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.

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 fluid, which in the event of a leak can pass through the sealing ring 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.

The sealing ring may, for example, be arranged in a groove machined into the wall of the through-channel, and the valve element may be reciprocable relative to the sealing ring, the sealing ring sealingly bearing against the circumference of the valve element.

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.

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.

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.

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 through-channel 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.

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.

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, s -that the desired stroke of the valve element can be structurally determined by the position of the stop.

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 face in the open position of the relief valve.

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.

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.

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. 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.

The return spring is preferably clamped between a collar of the valve element and an end face of the second housing part.

Figur 1:

eine schematische Seitenansicht eines erfindungsgemäßen Hoch- druckreinigungsgerätes;

Figur 2:

eine vergrößerte Längsschnittansicht des Pumpenkopfes des Hochdruckreinigungsgerätes aus Figur 1;

Figur 3:

eine Längsschnittansicht einer ersten Ausführungsform eines Ent- lastungsventils des Hochdruckreinigungsgerätes aus Figur 1 und

Figur 4:

eine Längsschnittansicht einer zweiten Ausführungsform eines Entlastungsventils des Hochdruckreinigungsgerätes aus Figur 1.

The following description of two preferred embodiments of the invention is used in conjunction with the drawings for further explanation. Show it:

FIG. 1:

a schematic side view of a high-pressure cleaning device according to the invention;

FIG. 2:

an enlarged longitudinal sectional view of the pump head of the high-pressure cleaner from FIG. 1 ;

FIG. 3:

a longitudinal sectional view of a first embodiment of a relief valve of the high-pressure cleaner from FIG. 1 and

FIG. 4:

a longitudinal sectional view of a second embodiment of a relief valve of the high-pressure cleaner from FIG. 1 ,

In the Figures 1 and 2 schematically a high-pressure cleaner 10 is shown with a device housing 12 which receives a motor pump unit 14. The latter comprises an electric motor 15, an adjoining gear 16 and a piston pump 18 driven by a swash plate 17 with a plurality of pistons 19 reciprocally displaceable in the axial direction of the high-pressure cleaning device 10. These submerge into a pump chamber 21 of a pump head 22 of the high-pressure cleaning device 10 one. 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 here all-pumping chambers 21 of the pump head 22 together.

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 ,

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.

The relief valve 38 is in FIG. 3 shown enlarged. 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.

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 passageway 50 valve member 61. The closing body 60 is configured in the form of a spherical cap and lies in the in FIG. 3 shown closed position of the relief valve 38 sealingly against the valve seat 58. 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.

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. 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 tight against the valve seat 58, as in FIG. 3 is shown.

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 element-61, when it lifts off 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 channel section 56 of the through-channel 50 a radially extending outlet 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 region adjoining the closing body 60, 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.

During normal operation of the high pressure cleaner 10, i. 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.

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 Longitudinal ribs 74 thus limit the stroke movement of the valve element 61.
By lifting the valve element 61 from the valve seat 58, the flow connection between the valve inlet 52 and the second valve outlet 89 is released, wherein within the inlet portion 91 of the passage channel 50, a considerable pressure sets, whereas in the outlet region 92 of the passage channel 50, by means of the sealing ring 66 is separated from the inlet portion 91, a considerably lower pressure is present, 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 portion 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 FIG. 4 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 cleaning device 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.

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.

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.

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.

Within the passage 107, a valve element 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 located in the in Figure 4 illustrated closed position of the relief valve 98 at one of the first conical extension 112 formed valve seat 136 close to. 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 valve element 132 surrounding circumferentially sealing ring 139 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 FIG FIG. 4 is shown. On the outside, the sealing ring 139 is tight against the wall of the fourth channel section 120.

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 pressure spring 134 in the third channel section 115 surrounding in the circumferential direction, designed as a helical spring return spring 146 is supported on the one hand on the valve seat 136 facing the free end face 148 of the cup-shaped insert 119 and on the other hand on the valve seat 136 facing away from bottom 149 of the collar 144. 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.

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 (12)

1. High-pressure cleaning appliance with a high-pressure pump, comprising at least one pump chamber which is connected to a suction line and a pressure line, the pressure line being in flow connection with the suction line via a return flow line, and a relief valve being arranged in the return flow line, the relief valve having a through-channel, which extends from a valve inlet to a first valve outlet, and which forms a valve seat, at least one outlet channel, which opens into a second valve outlet, branching off from the through-channel downstream of the valve seat, and a valve element adapted to be positioned by a return spring in a sealing manner against the valve seat being held for movement in the through-channel, characterized in that in the direction away from the valve seat (58; 136), at a spacing from the at least one outlet channel (88; 142), the valve element (61; 132) is surrounded by a sealing ring (66; 139) which seals off an inlet area (91, 154) of the through-channel (50; 107) adjacent to the valve inlet (52; 109) from an outlet area (92, 155) of the through-channel (50; 107) adjacent to the first valve outlet (75; 151).
2. High-pressure cleaning appliance in accordance with claim 1, characterized in that the sealing ring (66; 139) is arranged in a circumferential groove (64; 138) of the valve element (61; 132).
3. High-pressure cleaning appliance in accordance with 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. High-pressure cleaning appliance in accordance with claim 1, 2 or 3, characterized in that the valve element (61; 132) comprises a closure member (60; 133) which is adapted to be positioned in a sealing manner against the valve seat (58; 136), and a pressure member (63; 134) which is surrounded by the sealing ring (66; 139) at a spacing from the closure member (60; 133).
5. High-pressure cleaning appliance in accordance with claim 4, characterized in that the through-channel (50; 107) comprises a guide section (56; 120), on the inner wall of which the pressure member (63; 134) is mounted for displacement, with the sealing ring (66; 139) disposed between these.
6. High-pressure cleaning appliance in accordance with any one of the preceding claims, characterized in that the flow cross section of the through-channel (50; 107) in the area upstream of the at least one outlet channel (88; 142) is greater than the flow cross section of the outlet channel (88; 142).
7. High-pressure cleaning appliance in accordance with any one of the preceding claims, characterized in that the relief valve (38; 98) comprises a single outlet channel (88; 142).
8. High-pressure cleaning appliance in accordance with any one of the preceding claims, characterized in that the valve element (61; 132) at least partially opens the at least one outlet channel (88; 142) in both the open position and the closed position of the relief valve (38; 98).
9. High-pressure cleaning appliance in accordance with any one of the preceding claims, characterized in that the valve element (61; 132) has associated with it a stop (80; 126) on which the valve element (61; 132) bears when the relief valve (38; 98) is in the open position.
10. High-pressure cleaning appliance in accordance with claim 9, characterized in that the stop is formed by a narrowing (126) of the through-channel (107).
11. High-pressure cleaning appliance in accordance with claim 9, characterized in that the stop (80) is formed by a supporting element (74) which projects into the through-channel (50).
12. High-pressure cleaning appliance in accordance with any one of the preceding claims, characterized in that the relief valve (98) comprises a first housing part (101) and a second housing part (102), which are connectable to each other with a sealing ring (130) disposed between these.

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