EP3645885B1 - Appareil de nettoyage à haute pression - Google Patents

Appareil de nettoyage à haute pression Download PDF

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Publication number
EP3645885B1
EP3645885B1 EP17734301.9A EP17734301A EP3645885B1 EP 3645885 B1 EP3645885 B1 EP 3645885B1 EP 17734301 A EP17734301 A EP 17734301A EP 3645885 B1 EP3645885 B1 EP 3645885B1
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EP
European Patent Office
Prior art keywords
pressure
valve
chamber
overflow
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17734301.9A
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German (de)
English (en)
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EP3645885A1 (fr
Inventor
Andreas HÄGELE
Johannes Götz
Werner Schwab
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
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Alfred Kaercher SE and Co KG
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Publication of EP3645885A1 publication Critical patent/EP3645885A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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

Definitions

  • the invention relates to a high-pressure cleaning device with a pump for conveying a cleaning liquid, the pump having a suction line and a pressure line and a check valve being arranged in the pressure line, and the pump having an overflow valve which, depending on the pressure prevailing in the pressure line, of the Cleaning fluid releases a flow path via an overflow line for cleaning fluid to flow out of the pressure line, the overflow valve having a closing body which is in a closed position and which is liquid-tight against a valve seat and which can be moved against the closing force of a closing spring into an open position that is spaced from the valve seat and which with is connected to a control piston which is held displaceably in a control chamber and can be acted upon by cleaning fluid under pressure.
  • a cleaning liquid preferably water
  • the high-pressure cleaning device has a pump which can be driven by a motor, preferably an electric motor, and which has at least one piston which can be moved back and forth and which is immersed in a pump chamber.
  • the pump comprises three reciprocating pistons, each of which is immersed in a pump chamber.
  • Cleaning liquid to be pressurized can be fed to the pump via a liquid supply line, for example via a suction hose, and the pressurized cleaning liquid can be supplied from the pump via a liquid delivery line, for example via a high pressure hose, to a liquid delivery device, for example a spray gun or a spray lance .
  • the liquid dispensing member has a valve that can be opened and closed by the user. When the valve is open, the pressurized cleaning fluid can be dispensed, and the liquid dispensing can be stopped by closing the valve.
  • the high-pressure cleaning device has an overflow valve which opens depending on the pressure prevailing in the pressure line and releases a flow path so that cleaning fluid can flow out of the pressure line via an overflow line in order to lower the pressure in the pressure line. If the valve of the liquid dispensing element is closed, the pressure of the cleaning liquid in the pressure line increases due to the continued activity of the pump. When a predetermined maximum value of the pressure is exceeded, the overflow valve releases a flow path so that cleaning fluid can flow out of the pressure line via an overflow line.
  • the flow path extends from the pressure line via the overflow line to the suction line, so that when a predetermined maximum value of the pressure prevailing in the pressure line is exceeded, the overflow valve opens and cleaning fluid can flow from the pressure line via the overflow line to the suction line.
  • the pump can thus be operated in a circuit.
  • the flow path extends from the pressure line via the overflow line to an outlet via which cleaning fluid can be dispensed when a predetermined maximum value of the pressure prevailing in the pressure line is exceeded.
  • the flow path extends from the pressure line to a collecting space which, when the pressure prevailing in the pressure line is exceeded, receives cleaning fluid from the pressure line.
  • the pump is switched off after opening the overflow valve.
  • the overflow valve has a closing body which, in a closed position, rests against a valve seat in a liquid-tight manner and can be moved into an open position against the closing force of a closing spring, in which it is spaced from the valve seat and thereby clears the flow path from the pressure line via the overflow line.
  • the closing body is controlled with the aid of a control piston which is rigidly connected to the closing body via a valve rod and which can be acted upon with pressurized cleaning fluid.
  • a high-pressure cleaning device of the type mentioned above is from the WO 2016/015763 A1 known.
  • the pressure prevailing in the pressure line when cleaning fluid is dispensed acts on one side of the control piston and the closing force of the closing spring acts on the control piston on the opposite side.
  • the closing force of the closing spring thus counteracts the compressive force that results from the application of the pressure of the cleaning fluid in the pressure line to the control piston.
  • the pressure of the cleaning liquid can be more than 100 bar, in particular at least 150 bar.
  • an overflow valve arrangement for a high-pressure cleaning device is known, a control piston being displaceably mounted in a control chamber and dividing the control chamber into an outlet pressure chamber and an ambient pressure chamber.
  • the outlet pressure chamber has a first passage opening through which a piston rod fixed on the control piston penetrates in a liquid-tight manner.
  • the ambient pressure chamber has a second passage opening through which an actuating rod penetrates in a liquid-tight manner.
  • the ambient pressure chamber is connected to the ambient atmosphere via a ventilation opening.
  • the second passage opening has the same size as the first passage opening.
  • a high-pressure cleaning device in which an overflow valve can be actuated as a function of the flow rate of the cleaning liquid in the pressure line.
  • a throttle element in the form of an injector is arranged in an area of the pressure line downstream of the check valve, which has a through-hole that initially narrows in the direction of flow and then widens again, from the narrowest point of which a cross-hole branches off.
  • the pressure of the cleaning fluid in the transverse bore depends on its flow rate and is used to control the overflow valve.
  • the closing spring of the overflow valve can be made weaker and of a smaller size, but the use of the injector results in not insignificant flow losses, since the injector represents a not insignificant flow resistance. This in turn leads to higher energy consumption by the high-pressure cleaning device.
  • the high-pressure cleaning device has an overflow valve which is actuated with the aid of a control piston which is connected to the closing body of the overflow valve via a valve rod and which has a control chamber divided into an outlet pressure chamber and an overflow chamber.
  • the outlet pressure chamber is connected via a pressure channel to the transverse bore of the injector arranged downstream of a check valve in the pressure line and has a first passage opening which is tightly closed by means of a sealing plug.
  • the overflow valve chamber is connected via a line section of an overflow valve line to an area of the pressure line arranged upstream of the check valve and has a second passage opening which forms the valve seat of the overflow valve.
  • the first passage opening is larger than the second passage opening.
  • the control piston can be acted upon by the closing force of a closing spring.
  • the object of the present invention is to develop a high-pressure cleaning device of the type mentioned at the beginning in such a way that the size of the overflow valve can be reduced without using an injector and the assembly of the high-pressure cleaning device can be simplified.
  • control chamber is divided by the control piston into an outlet pressure chamber and an overflow chamber.
  • the control piston is preferably surrounded in the circumferential direction by a sealing element, for example a sealing ring, which seals the outlet pressure chamber from the overflow chamber.
  • the outlet pressure chamber can be acted upon by the pressure prevailing in the pressure line downstream of the check valve.
  • it is connected via a pressure channel to an area of the pressure line arranged downstream of the check valve.
  • the overflow chamber forms an area of the overflow line. It is via a section of the line Overflow line connected to an area of the pressure line arranged upstream of the check valve.
  • the overflow chamber can consequently be acted upon by the pressure prevailing in the pressure line upstream of the check valve.
  • the pressure prevailing in the pressure line downstream of the check valve is identical to the pressure prevailing in the pressure line upstream of the check valve, apart from slight pressure losses which the cleaning fluid suffers when flowing through the check valve.
  • practically the same pressures prevail in the outlet pressure chamber and the overflow chamber, with a first piston side of the control piston being subjected to the pressure prevailing in the outlet pressure chamber, and a second piston side of the control piston facing away from the first piston side with the in the pressure prevailing in the overflow chamber is applied.
  • the outlet pressure chamber has a first passage opening which is liquid-tight by a piston rod attached to the control piston is penetrated.
  • the piston rod extends from the control piston through the outlet pressure chamber to the first passage opening. This reduces the area of the control piston in the outlet pressure chamber that can be subjected to pressure in the direction of the overflow chamber.
  • the larger the first passage opening the smaller the area that can be acted upon with pressure, since this is reduced by the piston rod reaching through the first passage opening. This in turn has the consequence that the pressure force which acts on the control piston in the outlet pressure chamber and is oriented in the direction of the overflow chamber is reduced.
  • the overflow chamber also has a passage opening, which is referred to here as the second passage opening.
  • the second passage opening forms the valve seat of the overflow valve. While the cleaning fluid is being dispensed, the closing body of the overflow valve rests against the valve seat. The closing body is connected to the control piston via the valve rod. The valve rod extends from the control piston through the overpressure chamber to the closing body resting on the valve seat of the second passage opening. This reduces the area of the control piston in the overflow chamber that can be pressurized in the direction of the outlet pressure chamber, and consequently the pressure force acting on the control piston in the overflow chamber and directed towards the outlet pressure chamber is also reduced.
  • one of the two passage openings is larger than the other passage opening, for example the first passage opening.
  • the side of the control piston facing the larger passage opening is subject to a smaller pressure load than the side facing the smaller passage opening.
  • the resulting pressure load which acts on the control piston and causes it to shift, results from the difference in the pressure loads that act on the control piston in the outlet pressure chamber and the overflow chamber. From the different sizes of the two Passage openings result in a resulting pressure load which causes the control piston to shift in the direction of the larger passage opening. This resulting pressure load is counteracted by the closing force of the closing spring, which acts on the control piston on the side facing the larger passage opening.
  • the closing force which is required to keep the closing body reliably in its closed position during the discharge of cleaning liquid can consequently be kept low.
  • the only decisive factor for the strength of the required closing force is the difference in the pressure forces that act on the control piston in the outlet pressure chamber and the overflow chamber.
  • the size difference between the two passage openings is in turn important for this difference. The smaller the difference in size, the lower the clamping force required.
  • the pressure forces are dependent on the pressure of the cleaning fluid in the pressure line.
  • the greater the pressure the greater the pressure forces acting on the control piston.
  • the closing force exerted on the control piston by the closing spring is independent of the pressure of the cleaning fluid. If the pressure in the pressure line exceeds a predetermined maximum value, then the closing force exerted by the closing spring on the control piston is no longer sufficient to hold the control piston in place, rather the control piston then moves under the effect of the pressure load, and that via the valve rod with the control piston
  • the connected closing body lifts off the valve seat and releases the flow path from the pressure line via the overflow line, so that cleaning fluid can flow out of the pressure line and thereby the pressure in the pressure line can be reduced.
  • the closing spring In order to keep the closing body in its closed position, the closing spring only has to apply a closing force to the control piston, which is rigidly connected to the closing body via the valve rod, which corresponds to the difference in the pressure forces acting on the control piston.
  • This allows the use of a closing spring with a relatively small size, without an injector having to be arranged in the pressure line for this purpose.
  • the flow losses of the cleaning liquid under pressure can be kept low.
  • the closing spring is preferably arranged in the overflow chamber.
  • the closing spring is clamped between the control piston and a valve seat element, the valve seat element forming the second passage opening and the valve seat
  • the control piston carries the valve rod on its side facing the second passage opening, the valve rod reaching through the overflow chamber and the second passage opening and carrying the closing body in its area protruding from the overflow chamber, and the valve seat on the one facing away from the overflow chamber Side of the valve seat element is arranged and the closing body can be acted upon against the closing force of the closing spring with the pressure of the cleaning fluid prevailing in the overflow chamber.
  • the closing body is arranged on the side of the valve seat element facing away from the overflow chamber and, in the closed position, is acted upon by the pressure prevailing in the overflow chamber via the second passage opening. This application of pressure is directed against the closing force of the closing spring.
  • the pressure acting on the closing body acts on the control piston via the valve rod, so that the latter is not only subject to the pressure forces acting directly on it, but also the pressure force acting on the closing body.
  • the closing spring is advantageously designed as a helical spring which surrounds the valve rod.
  • the piston rod and the valve rod are cylindrical and have different diameters.
  • the diameter of the piston rod is greater than the diameter of the valve rod.
  • a sliding sleeve in which the control piston is displaceably mounted, is arranged in the control chamber.
  • the control piston preferably carries a sealing ring which rests on the sliding sleeve in a liquid-tight manner.
  • the sealing ring surrounding the control piston in the circumferential direction slides along the sliding sleeve when the control piston is displaced, and the frictional forces between the sealing ring and the sliding sleeve can be kept low by selecting a suitable material. When worn, the sliding sleeve can be easily replaced.
  • the sliding sleeve is preferably at least partially, in particular completely, made of a plastic material or of metal.
  • control piston has a first piston part and a second piston part rigidly connected to the first piston part.
  • the two piston parts are advantageously releasably connectable to one another.
  • the two piston parts can be screwed together.
  • the piston rod is conveniently arranged on the first piston part.
  • the first piston part is preferably connected in one piece to the piston rod.
  • the first piston part and the piston rod preferably form a one-piece component made of metal or a plastic material.
  • the valve rod is conveniently arranged on the second piston part.
  • the second piston part is integrally connected to the valve rod.
  • the second piston part is connected to the valve rod in a detachable or non-detachable manner.
  • the second piston part can be screwed to the valve rod.
  • a pressure relief valve is integrated into the control piston, which opens a flow path between the outlet pressure chamber and the overflow chamber depending on the pressure difference between the pressure of the cleaning fluid in the outlet pressure chamber and the pressure in the overflow chamber. If the pressure difference reaches a predetermined limit value, pressure compensation can take place via the pressure relief valve in that the pressure relief valve opens. If the pressure difference is less than the specified limit value, the pressure relief valve is closed.
  • the outlet pressure chamber is connected via a pressure channel to an area of the pressure line arranged downstream of the check valve.
  • the overflow chamber is connected via a first line section of the overflow line to an area of the pressure line arranged upstream of the check valve.
  • a second line section of the overflow line preferably adjoins the valve seat of the overflow valve and the flow connection between the overflow chamber and the second line section of the overflow line can be released and interrupted with the aid of the overflow valve depending on the pressure of the cleaning fluid.
  • Pressurized cleaning liquid can be fed to a liquid discharge element, for example a spray gun or a spray lance, via the pressure line and a liquid delivery line connected to the pressure connection of the high pressure cleaning device.
  • the pressurized cleaning liquid flows through the pressure line, the check valve being opened and the overflow valve is closed. If the liquid dispensing element is closed, the pressure of the cleaning liquid increases due to the activity of the pump in the pressure line. If the pressure of the cleaning liquid exceeds a predetermined maximum value, the overflow valve opens and cleaning liquid can flow out of the pressure line via the overflow line, for example to the suction line.
  • the check valve moves into its closed position and thus interrupts the flow connection between the area of the pressure line arranged upstream of the check valve and the area of the pressure line arranged downstream of the check valve.
  • the pressure relief valve is preferably integrated in the control piston, which, due to the high pressure prevailing downstream of the check valve in the pressure line, changes to its open position and thus a flow connection between the outlet pressure chamber and the overflow chamber releases.
  • the pressure of the cleaning fluid prevailing downstream of the check valve can be reduced by allowing cleaning fluid to flow from the area of the pressure line downstream of the check valve via the pressure channel, the outlet pressure chamber and the open pressure relief valve to the overflow chamber and from there via the second line section of the overflow line to the suction line, for example.
  • the pressure in the liquid discharge line for example a high-pressure hose, is lowered. This makes it easier for the user to then open the liquid dispensing member again.
  • the pressure relief valve integrated in the control piston preferably has a valve body which can be acted upon by a valve spring with a closing force, under the action of which the valve body rests on a valve seat. If the pressure of the cleaning fluid prevailing in the pressure line downstream of the check valve exceeds a predetermined value, the valve body of the pressure relief valve counteracts the action of the Valve spring into an open position in which it releases the flow path between the outlet pressure chamber and the overflow chamber.
  • the pump has a valve chamber into which an overflow device having the overflow valve can be inserted in the form of a subassembly that can be preassembled.
  • the preassembled assembly preferably has the valve seat element and the closing body of the overflow valve, the control piston and the piston rod, the valve rod and also the closing spring, which is supported on the one hand on the control piston and on the other hand on the valve seat element.
  • a pressure relief valve can be integrated into the control piston.
  • the high-pressure cleaning device 10 has a motor 12 which drives a pump 14 and, in the exemplary embodiment shown, is designed as an electric motor.
  • the pump 14 has a cylinder head 16 which forms a plurality of pump chambers, with only one of a total of three pump chambers in the drawing to achieve a better overview is shown schematically and assigned the reference numeral 18.
  • the pump chamber 18 is connected to a suction connection 26 via an inlet valve 22 and a suction line 24, and the pump chamber 18 is connected to a pressure connection 32 via an outlet valve 28 and a pressure line 30.
  • a liquid supply line for example a suction hose, which is known per se and is therefore not shown to achieve a better overview, can be connected to the suction connection 26 in the usual way, via which cleaning liquid to be pressurized, preferably water, can be supplied to the pump 12.
  • a liquid delivery line for example a high-pressure hose, which is known per se and is therefore not shown in the drawing to achieve a better overview, can be connected to the pressure connection 32 in the usual way, which has a closable liquid delivery element at its free end, for example a spray gun or a spray lance.
  • Cleaning liquid which has been pressurized by the pump 14, can be supplied to the liquid discharge element via the liquid discharge line.
  • a check valve 34 which is preferably designed without a spring and has a check valve body 36, is arranged in the pressure line 30.
  • the non-return valve body 36 can be placed in a liquid-tight manner against a non-return valve seat 40 with the interposition of a sealing ring 38 and can assume an open position (not shown in the drawing) for dispensing pressurized cleaning liquid, in which it is arranged at a distance from the non-return valve seat 40.
  • the cylinder head 16 has a stepped valve chamber 42, which can be closed in a liquid-tight manner with the aid of a sealing plug 44 and into which an overflow device 46 in the form of a preassembled structural unit is inserted.
  • the valve chamber 42 has a first, inwardly directed step 48 at a distance from the closure plug 44, and at a distance from the first step 48, the valve chamber 42 has a second, inwardly directed step 50.
  • the valve chamber 42 is cylindrical and in the area between the sealing plug 44 and the first step 48 receives a sliding sleeve 52 which rests against the wall of the valve chamber 42 with a sealing ring 54 in between.
  • the sliding sleeve 52 is made of a plastic material. It could also be made of a metal.
  • the sliding sleeve 52 surrounds a control chamber 56 in the area between the sealing plug 44 and the first step 48, which extends up to the second step 50 and in which a control piston 58 is held displaceably parallel to a longitudinal axis 60 of the valve chamber 42.
  • the control piston 58 has an annular groove which extends over the outer circumference of the control piston 58 and in which a second sealing ring 62 is arranged, which rests against the sliding sleeve 52 in a liquid-tight manner.
  • the control piston 58 divides the control chamber 56 into an outlet pressure chamber 64 and an overflow chamber 66.
  • the outlet pressure chamber 64 is arranged between the control piston 58 and the sealing plug 44 and connected via a pressure channel 68 to an area of the pressure line 30 arranged downstream of the check valve 34.
  • the overflow chamber 66 is arranged between the control piston 58 and a valve seat element 70 arranged on the second stage 50 and is connected via a first line section 72 of an overflow line 74 to an area of the pressure line 30 arranged upstream of the check valve 34.
  • a second line section 76 of the overflow line 74 connects to the second stage 50 of the valve chamber 42 and opens into the suction line 24.
  • valve seat element 70 is surrounded by a third sealing ring 78 which rests against the wall of the valve chamber 42 in a liquid-tight manner.
  • the control piston 58 On its side facing the outlet pressure chamber 64, the control piston 58 carries a piston rod 94 which is aligned coaxially with the longitudinal axis 60 of the valve chamber 42.
  • the sealing plug 44 has a first passage opening 96 which is oriented coaxially to the longitudinal axis 60.
  • the piston rod 94 extends through the outlet pressure chamber 64 and the first passage opening 96, being surrounded by a fourth sealing ring 98. With a free end 100 facing away from the control piston 58, the piston rod 94 protrudes from the outlet pressure chamber 64.
  • the valve seat element 70 has a second passage opening 80 which is aligned coaxially to the longitudinal axis 60 of the valve chamber 42 and which forms a valve seat 82 of an overflow valve 84 at its end facing the second line section 76 of the overflow line 74.
  • a closing body 86 of the overflow valve 84 which widens conically in the direction of the second line section 76, lies in one of the Figures 2 and 3rd the closed position shown in a liquid-tight manner on the valve seat 82.
  • the closing body 86 is rigidly connected to the control piston 58 via a valve rod 88.
  • valve rod 88 is aligned coaxially to the longitudinal axis 60, extends through the overflow chamber 66 and the second passage opening 80 and protrudes with its free end 90 facing away from the control piston 58 into the second line section 76 of the overflow line 74.
  • valve rod 88 is surrounded by a closing spring 92 designed as a helical spring, which is clamped between the control piston 58 and the valve seat element 70 and applies a closing force to the control piston 58.
  • the piston rod 94 like the valve rod 88, has a cylindrical design, the diameter of the piston rod 94 being greater than the diameter of the valve rod 88 second passage opening 80 designed cylindrically.
  • the diameter of the first passage opening 96 is only slightly larger than the diameter of the piston rod, whereas the diameter of the second passage opening 80 is significantly larger than the diameter of the valve rod 88.
  • the valve rod 88 is surrounded by an annular space 89, above to which an annular surface 91 of the closing body 86 can be acted upon by the pressure of the cleaning fluid prevailing in the overflow chamber 66.
  • the diameter of the first passage opening 96 is smaller than the diameter of the second passage opening 80 and thus also smaller than the diameter of the valve seat 82.
  • the diameter of the first passage opening 96 can be, for example, 4.0 mm and the diameter of the second passage opening 80 and the valve seat 82 can be, for example, 4.3 mm.
  • the control piston 58 has a first piston part 102 and a second piston part 104.
  • the first piston part 102 is integrally connected to the piston rod 94 and, together with the piston rod 94, forms a one-piece component made of metal or a plastic material.
  • the second piston part 104 forms an annular piston section 106 which carries the second sealing ring 62 on its outside and to which a piston shaft 108 is connected in one piece.
  • the piston shaft 108 is rigidly connected to the valve rod 88 via a screw connection 110.
  • the first piston part 102 has a piston sleeve 112 which plunges into the annular piston section 106 of the second piston part 104 and is releasably connected to the second piston part 104 via a screw connection with a fifth sealing ring 114 interposed.
  • a pressure relief valve 116 is integrated into the control piston 58 and has a spherical valve body 118 which is pressed by a valve spring 120 against a valve seat 122.
  • the first piston part 102 has a first radial bore 124, which is adjoined by a stepped axial bore 126 which extends axially through the piston sleeve 112 and which forms the valve seat 122.
  • the outlet pressure chamber 64 Via the first radial bore 124, the axial bore 126 and a second radial bore 128 of the second piston part 104, the outlet pressure chamber 64 is in flow connection with the overflow chamber 66, the flow connection by means of the spring-loaded valve body 118 depending on the pressure difference between that in the outlet pressure chamber 64 and the The pressure of the cleaning fluid prevailing in the overflow chamber 66 can be released and interrupted.
  • the outlet pressure chamber 64 and thus also the first piston side 132 of the control piston 58 facing the outlet pressure chamber 64 can be acted upon via the pressure channel 68 with the pressure of the cleaning fluid in the pressure line 30 downstream of the check valve 34.
  • the overflow chamber 66 and thus also the second piston side 134 of the control piston 58 facing the overflow chamber 66 can be acted upon by the cleaning fluid pressure upstream of the check valve 34 via the first line section 72 of the overflow line 74.
  • the pressure of the cleaning fluid acting on the first piston side 132 exerts a first pressure force on the control piston 58, which is aligned parallel to the longitudinal axis 60 and counteracts the closing force of the closing spring 92, and the pressure of the cleaning liquid acting on the second piston side 134 exerts a A second pressure force directed parallel to the longitudinal axis 60 and directed opposite to the first pressure force.
  • the control piston 58 is subjected to a compressive force resulting from the action of the pressure that acts on the annular surface 91 in the closed position of the closing body 86 and is transmitted to the control piston 58 via the valve rod 88.
  • the non-return valve 34 is opened, and the one upstream of the check valve 34 in the pressure line 30 is the same pressure of the cleaning fluid as the pressure of the cleaning fluid downstream of the check valve 34 in the pressure line 30, apart from slight pressure losses which the cleaning fluid suffers when the pressure flows through the springless check valve 34.
  • the outlet pressure chamber 64 that also prevails in the overflow chamber 66 and the pressure forces acting on the control piston 58 result from the sizes of the first piston side 132 and the second piston side 134 and the annular surface 91 of the closing body 86, which is connected to the the pressure prevailing in the overflow chamber 66 is applied.
  • the diameter of the valve seat 82 of the overflow valve 84 is larger than the diameter of the first passage opening 96, whereas the two piston sides 132, 134 are of the same size. This has the consequence that the control piston 58 is acted upon by a resulting differential pressure force which is opposite to the closing force of the closing spring 92.
  • the closing spring 92 counteracts the acting pressure differential force in such a way that the closing body 86 reliably assumes its closed position while the pressurized cleaning liquid is being dispensed and consequently the flow connection from the pressure line 30 via the overflow line 74 to the suction line 24 is interrupted.
  • the closing force of the closing spring 92 required for this is relatively small, so that the closing spring 92 can have a small overall size.
  • an increasing pressure is established in the pressure line upstream and downstream of the check valve 34, provided that the pump 14 is not switched off.
  • the increasing pressure of the cleaning fluid acts via the pressure channel 68 and the outlet pressure chamber 64 on the first piston side 132 and via the first line section 72 of the overflow line 74 and the overflow chamber 66 on the second piston side 134 and on the cleaning fluid pressure in the overflow chamber 66 acted upon annular surface 91 of the closing body 86.
  • the increasing pressure of the cleaning liquid results in an increasing differential pressure force, which counteracts the closing force of the closing spring 92.
  • the control piston 58 is displaced against the closing force of the closing spring 92 in the direction of the valve seat element 70, so that the closing body 86 lifts off the valve seat 82 and assumes an open position.
  • a flow connection to the suction line 24 is thus released via the overflow line 74 and the opened overflow valve 84.
  • the pressure of the cleaning fluid prevailing in the pressure line upstream of the check valve 34 is significantly reduced. Due to the pressure drop in the area upstream of the check valve 34, the check valve 34 closes, so that a higher pressure acts in the outlet pressure chamber 64 than in the overflow chamber 66.
  • the pressure relief valve 116 opens by pushing the valve body 118 against the force of the valve spring 120 lifts off the valve seat 122 and thereby a flow path from the outlet pressure chamber 64 to the overflow chamber 66 is released via the first radial bore 124, the axial bore 126 and the second radial bore 128.
  • the pressure can thus also be reduced in the region of the pressure line 30 arranged downstream of the check valve 34. This makes it possible, in particular, to reduce the pressure in the liquid delivery line connected to the pressure connection 32.
  • the cleaning fluid is subject to only slight pressure losses when it flows through the pressure line 30. This reduces the energy consumption of the high-pressure cleaning device 10 when dispensing cleaning fluid.
  • the closing spring 92 can have a small overall size. This makes it possible to keep the overall size of the complete overflow device 46 small, wherein the overflow device 46 can be inserted into the valve chamber 42 in the form of a preassembled structural unit. This also simplifies the assembly of the high-pressure cleaning device 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Cleaning By Liquid Or Steam (AREA)

Claims (12)

  1. Appareil de nettoyage haute pression avec une pompe (14) pour refouler un liquide de nettoyage, dans lequel la pompe (14) présente une conduite d'aspiration (24) et une conduite de pression (30) et un clapet anti-retour (34) est disposé dans la conduite de pression (30), et dans lequel la pompe (14) présente une soupape de trop-plein (84), qui, en fonction de la pression du liquide de nettoyage régnant dans la conduite de pression (30), libère une voie d'écoulement par l'intermédiaire d'une conduite de trop-plein (74) pour l'écoulement du liquide de nettoyage à partir de la conduite de pression (30), dans lequel la soupape de trop-plein (84) présente un corps de fermeture (86), s'appliquant de manière étanche au liquide contre un siège de soupape (82) dans une position de fermeture, qui peut se déplacer à l'encontre de la force de fermeture d'un ressort de fermeture (92) dans une position d'ouverture espacée du siège de soupape (82) et qui est relié par l'intermédiaire d'une tige de soupape (88) à un piston de commande (58) retenu de manière coulissante dans une chambre de commande (56) et pouvant être soumis à l'effet d'un liquide de nettoyage sous pression, et dans lequel le piston de commande (58) divise la chambre de commande en une chambre de pression de sortie (64) et une chambre de trop-plein (66), dans lequel la chambre de pression de sortie (64) est reliée à une zone de la conduite de pression (30) disposée en aval du clapet anti-retour (34) par l'intermédiaire d'un canal de pression (68) et présente une première ouverture de passage (96), et dans lequel la chambre de trop-plein (66) est reliée à une zone de la conduite de pression (30) disposée en amont du clapet anti-retour (34) par l'intermédiaire d'une partie de conduite (72) de la conduite de trop-plein (74) et présente une deuxième ouverture de passage (80), qui réalise le siège de soupape (82), dans lequel les deux ouvertures de passage (96, 80) présentent une taille différente, caractérisé en ce que la première ouverture de passage (96) est traversée de manière étanche au liquide par une tige de piston (94) fixée sur le piston de commande (58) et le piston de commande (58) peut être soumis à l'effet de la force de fermeture du ressort de fermeture (92) sur sa face tournée vers l'ouverture de passage plus grande.
  2. Appareil de nettoyage haute pression selon la revendication 1, caractérisé en ce que le ressort de fermeture (92) est disposé dans la chambre de trop-plein (66) .
  3. Appareil de nettoyage haute pression selon la revendication 1 ou 2, caractérisé en ce que le ressort de fermeture est serré entre le piston de commande (58) et un élément de siège de soupape (70) qui réalise la deuxième ouverture de passage (80) et le siège de soupape (82) .
  4. Appareil de nettoyage haute pression selon la revendication 3, caractérisé en ce que le piston de commande (58) porte sur sa face (134) tournée vers la deuxième ouverture de passage (80) la tige de soupape (88), dans lequel la tige de soupape (88) traverse la chambre de trop-plein (66) et la deuxième ouverture de passage (80) et porte sur sa zone faisant saillie de la chambre de trop-plein (66) le corps de fermeture (86), et dans lequel le siège de soupape (82) est disposé sur la face de l'élément de siège de soupape (70) opposée à la chambre de trop-plein (66) et le corps de fermeture (86), à l'encontre de la force de fermeture du ressort de fermeture (92), peut être soumis à l'effet de la pression du liquide de nettoyage régnant dans la chambre de trop-plein (66).
  5. Appareil de nettoyage haute pression selon l'une quelconque des revendications précédentes, caractérisé en ce que la tige de piston (94) et la tige de soupape (88) sont conçues de manière cylindrique et présentent des diamètres différents.
  6. Appareil de nettoyage haute pression selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un coulisseau (52), dans lequel le piston de commande (58) est monté de manière coulissante, est disposé dans la chambre de commande (56).
  7. Appareil de nettoyage haute pression selon l'une quelconque des revendications précédentes, caractérisé en ce que le piston de commande (58) présente une première partie de piston (102) et une deuxième partie de piston (104) reliée rigidement à la première partie de piston (102) .
  8. Appareil de nettoyage haute pression selon la revendication 7, caractérisé en ce que la première partie de piston (102) est reliée d'une seule pièce à la tige de piston (94).
  9. Appareil de nettoyage haute pression selon la revendication 7 ou 8, caractérisé en ce que la deuxième partie de piston (104) est reliée de manière libérable ou non libérable, en particulier vissée, à la tige de soupape (88).
  10. Appareil de nettoyage haute pression selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une soupape de décharge de pression (116), qui, en fonction de la différence de pression entre la pression régnant dans la chambre de pression de sortie (64) et celle dans la chambre de trop-plein (66), libère un trajet d'écoulement entre la chambre de pression de sortie (64) et la chambre de trop-plein (66), est intégrée dans le piston de commande (58).
  11. Appareil de nettoyage haute pression selon la revendication 10, caractérisé en ce que la soupape de décharge de pression (116) présente un corps de soupape (118), qui peut être soumis par un ressort de soupape (120) à l'effet d'une force de fermeture, sous l'action de laquelle le corps de soupape (118) s'applique contre un siège de soupape (122).
  12. Appareil de nettoyage haute pression selon l'une quelconque des revendications précédentes, caractérisé en ce que la pompe (14) présente une chambre de soupape (42), dans laquelle un dispositif de trop-plein (46) présentant la soupape de trop-plein (84) peut être inséré sous forme d'un module pré-assemblé.
EP17734301.9A 2017-06-29 2017-06-29 Appareil de nettoyage à haute pression Active EP3645885B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2017/066187 WO2019001719A1 (fr) 2017-06-29 2017-06-29 Appareil de nettoyage à haute pression

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EP3645885A1 EP3645885A1 (fr) 2020-05-06
EP3645885B1 true EP3645885B1 (fr) 2021-06-02

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EP (1) EP3645885B1 (fr)
CN (1) CN110832200B (fr)
WO (1) WO2019001719A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102020131796A1 (de) 2020-12-01 2022-06-02 Alfred Kärcher SE & Co. KG Kolbenpumpe für ein hochdruckreinigungsgerät

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Publication number Priority date Publication date Assignee Title
CN111112194A (zh) * 2020-01-09 2020-05-08 绿田机械股份有限公司 一种无负载启动及自动启停的高压清洗机
CN112747581B (zh) * 2020-12-31 2023-03-28 北京中矿博能节能科技有限公司 多级多效网链闭式煤泥干燥***
CN113107799B (zh) * 2021-05-20 2022-12-16 浙江亿力机电股份有限公司 适用于高压清洁设备的活塞泵

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DE29716274U1 (de) * 1997-09-10 1999-01-14 Lorentz, Bernt, 22457 Hamburg Überströmventil
DE19838947C1 (de) * 1998-08-12 1999-11-25 Frank Arbeiter Bypassventilanordnung für ein Hochdruckreinigungsgerät sowie Hochdruckreinigungsgerät mit einer solchen Bypassventilanordnung
CN1302205C (zh) * 2004-05-12 2007-02-28 胡松海 差压式低保压关枪停机装置
CN2861665Y (zh) * 2005-12-22 2007-01-24 上海神龙清洗机有限公司 一种用于高压清洗机的溢流阀
DE102009049095A1 (de) * 2009-10-01 2011-04-07 Alfred Kärcher Gmbh & Co. Kg Pumpe für ein Hochdruckreinigungsgerät
DE102009049096A1 (de) 2009-10-01 2011-04-07 Alfred Kärcher Gmbh & Co. Kg Pumpe für ein Hochdruckreinigungsgerät
PL2805055T3 (pl) * 2012-01-20 2016-11-30 Pompa tłokowa dla urządzenia do czyszczenia wysokociśnieniowego
EP3175113A1 (fr) 2014-07-30 2017-06-07 Alfred Kärcher GmbH & Co. KG Pompe à piston et appareil de nettoyage à haute pression équipé d'une telle pompe à piston
CN205154198U (zh) * 2015-11-26 2016-04-13 山东瀚业机械有限公司 一种内注式单体液压支柱专用自动泄压阀

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020131796A1 (de) 2020-12-01 2022-06-02 Alfred Kärcher SE & Co. KG Kolbenpumpe für ein hochdruckreinigungsgerät

Also Published As

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WO2019001719A1 (fr) 2019-01-03
EP3645885A1 (fr) 2020-05-06
CN110832200B (zh) 2021-08-10
CN110832200A (zh) 2020-02-21

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