EP2817516B1 - Pompe pour un nettoyeur haute pression et un nettoyeur haute pression - Google Patents

Pompe pour un nettoyeur haute pression et un nettoyeur haute pression Download PDF

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Publication number
EP2817516B1
EP2817516B1 EP12705138.1A EP12705138A EP2817516B1 EP 2817516 B1 EP2817516 B1 EP 2817516B1 EP 12705138 A EP12705138 A EP 12705138A EP 2817516 B1 EP2817516 B1 EP 2817516B1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
line
axis
accordance
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
EP12705138.1A
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German (de)
English (en)
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EP2817516A1 (fr
Inventor
Ronald Krauter
Patrik KOEPPEN
Frank Heinrich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alfred Kaercher SE and Co KG
Original Assignee
Alfred Kaercher SE and Co KG
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Application filed by Alfred Kaercher SE and Co KG filed Critical Alfred Kaercher SE and Co KG
Publication of EP2817516A1 publication Critical patent/EP2817516A1/fr
Application granted granted Critical
Publication of EP2817516B1 publication Critical patent/EP2817516B1/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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04B17/06—Mobile combinations
    • 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
    • F04B53/22—Arrangements for enabling ready assembly or disassembly
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B2203/00—Details of cleaning machines or methods involving the use or presence of liquid or steam
    • B08B2203/02—Details of machines or methods for cleaning by the force of jets or sprays
    • B08B2203/0205—Bypass pressure relief 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 pump for a high-pressure cleaning device for conveying a cleaning liquid
  • the pump has a pump head comprising a base body in which a suction line and a connected thereto via at least one pumping pressure line is formed, a bypass line connecting the pressure line with the Suction line connects, is aligned transversely to the pressure line and defines a pumping plane therewith, and a discharge line connected to the pressure line for connecting an external fluid line
  • the pump head has an arranged on the bypass line spill valve, the valve body is connected to a piston which is connected to the the bypass line opposite side immersed in the pressure line, a portion of the pressure line in the flow direction with the discharge line via a pressure channel limited in sections and depending on the fluid pressure in the pressure chamber, the valve body to open n and closing the bypass line moves.
  • the invention relates to a high-pressure cleaning device.
  • a cleaning liquid in particular water can be pressurized and conveyed.
  • Water is supplied to the pump via the suction line, compressed in the pumping chamber and delivered to the pressure line.
  • the cleaning liquid to an external, connected to the pump head liquid line, such as a high-pressure hose, are discharged.
  • a pressure nozzle is arranged, for example, a connected high-pressure gun, which can be directed to an object to be cleaned.
  • the bypass line is provided, through which the pumped Cleaning fluid can be pumped in the pump in the circulation.
  • a pump of the type mentioned in which the pressure line and the bypass line are aligned transversely to each other and define a pump plane and the piston of the opposite side of the bypass line dips into the pressure line, characterized by a compact flat design using a small amount of material and by low processing and manufacturing costs.
  • the pump head is manufactured from the base body, into which bores are introduced for forming the respective fluid lines and fluid channels
  • a pressure relief valve on the pressure line, with which the pressure in the pressure line can be reduced when a maximum allowable pump pressure is exceeded. This can occur, for example, with a defective overflow valve.
  • a switch plunger for actuating an electrical switching element with which a drive motor for the pump is then turned off when the pressure nozzle is closed.
  • Such a switch plunger is arranged for example in a receiving space, which is fluidly connected to the pressure chamber, so that the switching plunger can be actuated depending on the fluid pressure in the pressure chamber.
  • Pumps for high-pressure cleaning devices are for example in the EP 0 668 113 A1 , in the DE 39 36 155 A1 and in the DE 10 2007 003 521 A1 described.
  • Object of the present invention is to develop a pump of the type mentioned, with the pump variants can be formed in a structurally simple manner, which include a pressure relief valve or a switching plunger for actuating an electrical switching element.
  • the integrally formed on the Grundköper approach may already be formed on a blank for the production of the pump head and in the construction of pump variants with pressure relief valve or switch plunger for actuating an electrical switching element are equally processed.
  • the first nose portion defines a first axis that intersects the pressure line.
  • a pump variant having a pressure relief valve can be structurally simply formed, in which a bore for receiving the pressure relief valve is introduced.
  • a pump variant can be formed in a structurally simple manner, which comprises a switching plunger for actuating an electrical switching element, in which a bore for receiving the switch plunger is introduced.
  • the two processing variants Due to the two processing variants, it is in particular not necessary to provide different blanks for the production of the base body. This reduces manufacturing costs, such as for tools, as well as storage costs.
  • the first axis and the second axis of the two axis sections intersect each other at an intersection point located outside the pressure line and the pressure chamber.
  • the approach can thereby be formed using only a small amount of material and allows a cost-effective production of the blank for the body.
  • In a processing of the body to form the two pump variants must also only a small amount of material is removed to form either a pump variant with a pressure relief valve or a pump variant with a switching tappet. This reduces the scrap of material and allows a rapid and cost-effective processing of the blank.
  • the positioning of the axis intersection point outside the pressure line and the pressure chamber allows a compact arrangement of the neck portions relative to each other. This allows a compact design of the respective pump variant achieved and the compact design of the pump of the type mentioned are maintained.
  • intersection angle between the first axis and the second axis is smaller than 90 °, preferably smaller than 60 °, more preferably smaller than 30 °.
  • the approach can be made structurally compact using as small a quantity of material as possible.
  • the angle is approximately 20 ° in order to achieve a particularly compact design.
  • first attachment portion and the second attachment portion define the first axis and the second axis, respectively, based on their outer contour. This makes it easier for an editor to process the approach. For the operator, the position and orientation of the axis defined by him can already be recognized on the basis of the outer contour of the respective projection section.
  • the first attachment portion and the second attachment portion are intersecting attachment portions having a cylindrical or substantially cylindrical outer contour.
  • the neck portions intersect, for example, at an angle of approximately 20 °.
  • the first lug portion and the second lug portion are intersecting lug portions having a cylindrical or substantially cylindrical outer contour. This makes it even easier for an operator to recognize the respective attachment section and the machining direction along the axis defined by the attachment section.
  • both neck portions are arranged in the pump plane in order to achieve a particularly compact design of the pump head.
  • first attachment section is arranged in the pump plane, its first axis expediently runs parallel to or in accordance with an axis defined by the pressure line.
  • the approach is formed on one side of the base body, along which the bypass line extends, and if the spill valve between the approach and a pressure line section of the pressure line is arranged, in the at least one outlet valve for sealing the at least one pumping chamber relative to Pressure line is arranged.
  • the approach and the at least one outlet valve receiving pressure line section are arranged on opposite sides of the bypass line and the spill valve.
  • the discharge line is aligned transversely to the pressure line. This simplifies the machining of the main body for forming the discharge line.
  • discharge line and the bypass line define a second pump plane oriented perpendicular to the pump plane.
  • approach and the pressure line are advantageously arranged on opposite sides of the second pump level and arranged in the first pump level, so that the pump head can be given a particularly compact design.
  • the first attachment portion has an axial bore along the first axis, in which a pressure relief valve is used, and when the bore is connected via a pressure relief passage to the pressure line.
  • the introduction of the axial bore in the first neck portion and the overpressure channel for connection to the pressure line is possible for a processor by the orientation of the first axis in a simple manner.
  • the pressure relief valve ensures that a pressure in the pressure line that exceeds a permissible pressure can be reduced. Under overpressure liquid can act on the pressure relief valve through the pressure relief valve so that it can be actuated and the pressure can be discharged.
  • the overpressure channel can be designed in a structurally simple manner if it runs as an axial channel along the first axis.
  • the overpressure channel may for example be connected to a section of the pressure line in which the valve body of the overflow valve is arranged and from which the bypass line branches off.
  • the discharge line branches off from the portion of the pressure line.
  • the second approach portion has an axial bore along the second axis, in which a switch plunger is inserted, and when the bore is connected via a switching channel with the pressure chamber, wherein the switch plunger depends on the pressure in the pressure chamber of a first Switching position in a second switching position and vice versa for actuating an electrical switching element is axially movable.
  • the switching plunger may have an active surface on its side facing the switching channel, which can be acted upon via the switching channel with the pressure in the pressure chamber in order to transfer the switching plunger from a first switching position to a second switching position.
  • the electric switching element can be actuated to turn off an engine driving the pump.
  • the switching plunger can be transferred from the second switching position to the first switching position and the engine thus be put back into operation.
  • the switching channel extends as an axial channel along the second axis, so that it can be formed in a simple manner.
  • the axial bore is connected via a compensation channel to the pressure line, via which the switch plunger is acted upon by an active surface with pressure of the liquid in the pressure line, which effective surface counteracts an effective surface of the switch plunger, via which the switch plunger with pressure of Liquid is applied in the pressure chamber.
  • the compensation channel is longitudinal or parallel to the first axis.
  • the pump has a switching ram and the electrical switching element comprehensive unit in the form of a pressure switch used in the axial bore.
  • the switch plunger and the electrical switch contact may be part of a preassembled unit, the faster assembly can be pre-assembled on the pump head and inserted into the axial bore.
  • An advantageous embodiment of the pump according to the invention is a crankshaft pump.
  • the pump is a swash plate pump.
  • the invention also relates to a high-pressure cleaning device.
  • An inventive high-pressure cleaning device has at least one pump of the aforementioned type.
  • FIG. 1 shows a perspective view obliquely from the front of a preferred embodiment of a total occupied by the reference numeral 10 high-pressure cleaning device.
  • the high-pressure cleaning device is configured as a "tube frame device” and comprises a motor pump unit 12.
  • the motor pump unit 12 has a motor 13 and a pump 14, which is flanged to drive it.
  • the pump 14 is designed as a crankshaft pump and comprises a pump block 15 connected to the motor 13 and a pump head 16 placed thereon.
  • the pump head 16 can be supplied via a pump inlet 17 under pressure liquid to be placed, in particular water.
  • a high-pressure gun 20 is connected to the high-pressure hose 19, the pressure nozzle 21 selectively opened by a user and can be closed.
  • the high-pressure cleaning device 10 has an electrical device 22, which is designed as a switching device and is connected to the motor 13 via an electrical connection line 23.
  • the electrical device 22 is connected via a further electrical connection line (partially shown) 24 with a pressure switch 25 which is connected to the pump head 16. On the pressure switch 25 will be discussed below.
  • the pump head 16 has a compact, flat construction and comprises a main body 26, are introduced into the bores for forming fluid lines and fluid channels.
  • a suction line 27 is formed in the main body, which opens via three inlet valves 28 in each case a pumping chamber 29.
  • liquid to be pressurized can be compressed by means of pistons 30.
  • the liquid is conveyed via outlet valves 31 into a pressure line 32 parallel to the suction line 27.
  • From the pressure line 32nd is the side of the high-pressure connection forming discharge line 18 from.
  • a bypass line 33 connects the pressure line 32 with the suction line 27 from the branch of the discharge line 18 to immediately behind the pump inlet 17th
  • the pressure line 32 has a first pressure line section 321, in which the outlet valves 31 are arranged and which defines the below-mentioned axis 50 of the pressure line 32, and a second pressure line section 322, from which the bypass line 33 and the discharge line 18 branch off.
  • the compact flat construction of the pump head 16 is achieved in that the pumping chamber 29, the pressure line 32 and the bypass line 33 are arranged in a common plane, the pump plane, in FIG. 3 in the drawing plane.
  • the bypass line 33 is aligned transversely to the pressure line 32 and transversely to the discharge line 18.
  • the discharge line 18 and the bypass line 33 span a further level, a second pump level, the in FIG. 4 in the drawing plane. This favors the compact construction of the pump head 16.
  • a piston 34 of a spill valve 35 in the pressure line section 322 of the pressure line 32 a is held, which can seal a valve seat 37 at the beginning of the bypass line 33 and release.
  • the piston 34 is slidably mounted in an insert 38 against the force of an elastic return element in the form of a spring 39.
  • the piston 34 is designed as a stepped piston, which limits a pressure chamber 40 distance.
  • the pressure chamber 40 is designed as an annular chamber and is connected via a pressure channel 41 with the discharge line 18 in fluid communication. ( FIG. 4 in which the connection of the pressure chamber 40 and the pressure channel 41 is not shown.)
  • a check valve 42 is also connected in the discharge line 18.
  • the Check valve 42 may seal a valve seat 43, which, based on the flow direction of the conveyed liquid, is arranged before the connection of the pressure channel 41 to the discharge line 18.
  • the check valve 42 seals the discharge line 18 from.
  • the excess pressure remaining in the high-pressure hose 19 forms a pressure surge through the pressure channel 41 into the pressure chamber 40, which acts on the piston 34.
  • the piston 34 is moved to lift the valve body 36 from the valve seat 37, so that the bypass line 33 is released.
  • the liquid is conveyed by the pump 14 to reduce the mechanical load between the suction line 27 and the pressure line 32 via the bypass line 33 in a circle.
  • bypass line 33 is closed when the pressure nozzle 21 is released, so that the piston 34 is moved back to its original position and further the check valve 42 opens.
  • FIG. 3 only partially shown pressure switch 25.
  • the pressure switch 25 is inserted into a molded onto the base 26 projection 44.
  • the projection 44 is arranged to achieve a compact construction of the pump head 16 in the pump plane defined by the pressure line 32 and the bypass line 33 and comprises two neck portions 45 and 46.
  • the neck portions 45 and 46 are configured here as a body, each cylindrical or substantially cylindrical Outer contour, whereby they define a first axis 47 and a second axis 48.
  • the outer contours of the neck portions 45 and 46 are in their extension in the Figures 3 and 5 shown on the right with dashed lines.
  • the neck portions 45 and 46 cross each other with their axes 47 and 48 intersect at an intersection 49 disposed outside the pressure line 32 and the pressure chamber 40.
  • the cutting angle between the axes 47 and 48 is presently about 20 °.
  • the projection 44 has, on the one hand, a compact design using a relatively small amount of material; on the other hand, the projection sections 45 and 46 can be detected in a simple manner and the position of the axes 47 and 48 can be detected.
  • the projection 44 is formed on the base body 26 to achieve a compact construction of the pump head 16 on the side along which the bypass line 33 extends, wherein the spill valve 35 is disposed between the projection 44 and the pressure line section 321, in which the outlet valves 31 are arranged.
  • the first axis 47 defined by the first attachment section 45 is aligned parallel to an axis 50 defined by the pressure line 32, in particular the pressure line section 321, and offset therefrom somewhat in the direction of the pressure chamber 40.
  • the first axis 47 traverses the pressure line section 322 on its side opposite the bypass line 33.
  • the first attachment section 45 is thus formed on the base body 26 in such a way that the first axis 47 intersects the pressure line 32 at the pressure line section 322.
  • the second projection portion 46 is formed on the base body 26 so that the second axis 48 passes through the pressure chamber 40 and cuts them.
  • an axial bore 51 is introduced along the axis 48, in which the pressure switch 25 is partially inserted.
  • the switching plunger 53 is supported via an elastic return element in the form of a spring 54 on the insert 52 from which he passes, so that he with his the pressure chamber 40 remote end can actuate an electrical switching element 55 of the pressure switch 25.
  • an axial switching channel 56 connects, via which the bore 51 is fluidly connected to the pressure chamber 40.
  • a compensation channel 57 is introduced into the first attachment section 45 parallel to the first axis 47. Via the compensation channel 57, the pressure line section 322 of the pressure line 32 is in fluid communication with the axial bore 51.
  • the compensation channel 57 opens into an annular space surrounding the insert 52 of the bore 51 which is in fluid communication with the space of the bore 51 accommodating the switch plunger 53.
  • On opposite effective surfaces 58 and 59 of the switching plunger 53 thereby act the pressure in the pressure chamber 40 and the pressure in the pressure line 32nd
  • the switching channel 56 and the compensation channel 57 ensure that upon closing the pressure nozzle 21 after opening the spill valve 35, the switch plunger 53 is axially displaced against the force of the spring 54 and the differential pressure of the pressure chamber 40 and the pressure line 32 to the switching element 55 actuate. This results in a switching pulse, which is transmitted from the pressure switch 25 for switching off the motor 13 to the electric device 22.
  • the pressure nozzle 21 is opened, the pressure in the pressure chamber 40 drops, and the switching plunger 53 is shifted back to the original position by operating the switching element 55 due to the differential pressure of the pressure line 32 and the pressure chamber 40 and the assisting force of the spring 54.
  • the electric device 22 receives a start pulse for turning on the motor 13, so that cleaning liquid can be conveyed again.
  • FIG. 5 in a sectional view in one of the FIG. 3 corresponding pump head 60 may be combined with the pump block 15 to form a second preferred embodiment of a pump according to the invention.
  • This pump can also be used in the high-pressure cleaner 10.
  • the same reference numerals are used for the same features of the pump heads 16 and 60.
  • the representation according to FIG. 4 is at the same time a sectional view along the line 4-4 in FIG. 5 ,
  • the pump head 60 is largely identical in construction to the pump head 16. From the pump head 16, the pump head 60 differs in that there is no pressure switch 25, but instead a pressure relief valve 61 and that this is used in the differently processed approach 44.
  • the projection 44 in the pump head 60 is externally largely identical to the projection 44 in the pump head 16. Except this is a projection 62 (FIG. FIG. 3 ), which is still present at the second end portion 46 at the end facing away from the pressure chamber 40 due to the processing, wherein the projection 62 at the pump head 60 due to the processing of the projection 44, however, is missing.
  • the first projection 45 has an axial bore 63 into which the pressure relief valve 61 is inserted.
  • the overpressure valve 61 comprises a closure element 64 closing the bore 63 at the end, on which a valve body 65 of the overpressure valve 61 is supported in the form of a spring 66 by means of an elastic restoring element.
  • the bore 63 is connected via an axial overpressure channel 67 to the pressure line section 322 of the pressure line 32, so that the pressure in the pressure line 32 acts on the valve body 65.
  • the pressure relief valve 61 is a safety valve. If the pressure in the pressure line 32 exceeds a maximum permissible value, the valve body 65 is displaced against the force of the spring 66. The spring 66 has a buffering action so that the sealing closure member 64 is not immediately squeezed out of its seat. However, this occurs when the allowable pressure is greatly exceeded or when the overpressure persists for a longer time. In both cases, the pressure relief valve 61 is pressed out of the bore 63, and liquid can escape from the pump head 60 via the overpressure passage 67 and the bore 63.
  • the projection 44 is integrally formed at both pump heads 16 and 60 to the base body 26 and has in each case the neck portions 45 and 46 which the Define axes 47 and 48.
  • This allows a structurally simple way to provide both the pump head 16 and the pump head 60 a common blank for the base body 26 for the production.
  • the axial bore 51, the switching channel 56 and the compensation channel 57 on the one hand or the axial bore 63 and the overpressure channel 67 on the other hand in the neck 44th and the main body 26 are introduced.
  • the manufacturing costs are also kept low by the oblique orientation of the neck portions 45 and 46 relative to each other.
  • the lug 44 has a compact construction that can be achieved with only a small amount of material.
  • the amount of material to be removed during the processing of the projection 44 for the production of the pump heads 16 or 60 is low, which in turn has an advantageous effect on the production costs.
  • the provision of the projection 44 with the neck portions 45 and 46 also facilitates the preparation of the pump heads 16 and 60. Through the respective cylindrical outer contour, an operator can determine the axes 47 and 48 in a simple manner. This makes it easier for him to form the holes 51 and 63 and the channels 56, 57 and 67 as needed in the neck portions 45 and 46.

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  • Reciprocating Pumps (AREA)

Claims (17)

  1. Pompe pour un appareil de nettoyage haute-pression (10) destinée à refouler un liquide de nettoyage, la pompe (14) présentant une tête de pompe (16) qui comprend un corps de base (26) dans lequel est formée une conduite d'aspiration (27) et une conduite de pression (32) reliée à la précédente par l'intermédiaire d'au moins une chambre de pompe (29), caractérisée en ce que dans le corps de base (26) est formée une conduite de dérivation (33), qui relie la conduite de pression (32) à la conduite d'aspiration (27), est orientée transversalement à la conduite de pression (32) et définit avec celle-ci un plan de pompe, ainsi qu'une conduite de distribution (18) reliée à la conduite de pression (32) et destinée au raccordement d'une conduite de liquide externe, la tête de pompe (16) comportant une soupape de décharge (35) agencée au niveau de la conduite de dérivation (33), dont le corps d'obturation de soupape (36) est relié à un piston (34), qui plonge dans la conduite de pression (32) à partir du côté opposé à celui où se trouve la conduite de dérivation (33), délimite partiellement une chambre de pression (40) en liaison d'écoulement avec la conduite de distribution (18) par l'intermédiaire d'un canal de pression (41), et qui déplace le corps d'obturation de soupape (36) en fonction de la pression de liquide dans la chambre de pression (40), pour ouvrir et fermer la conduite de dérivation (33), et sur le corps de base (26) étant formé un appendice (44) qui présente un premier tronçon d'appendice (45) définissant un premier axe (47) coupant la conduite de pression (32), ainsi qu'un deuxième tronçon d'appendice (46) définissant un deuxième axe (48) coupant la chambre de pression (40), le premier axe (47) et le deuxième axe (48) se coupant en un point d'intersection (49) situé à l'extérieur de la conduite de pression (32) et de la chambre de pression (40).
  2. Pompe selon la revendication 1, caractérisée en ce que l'angle d'intersection entre le premier axe (47) et le deuxième axe (48) est inférieur à 90°, de préférence inférieur à 60°, et de manière encore plus préférée inférieur à 30°.
  3. Pompe selon la revendication 2, caractérisée en ce que l'angle d'intersection est environ égal à 20°.
  4. Pompe selon l'une des revendications précédentes, caractérisée en ce que le premier tronçon d'appendice (45) et le deuxième tronçon d'appendice (46) définissent le premier axe (47) et respectivement le deuxième axe (48), au regard de leur contour extérieur.
  5. Pompe selon la revendication 4, caractérisée en ce que le premier tronçon d'appendice (45) et le deuxième tronçon d'appendice (46) sont des tronçons d'appendice (45, 46) mutuellement concourants, et se croisant notamment en croix, avec un contour extérieur cylindrique ou sensiblement cylindrique.
  6. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'un au moins des tronçons d'appendice (45, 46) est agencé dans le plan de pompe, notamment en ce que les deux tronçons d'appendice (45, 46) sont agencés dans le plan de pompe.
  7. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'appendice (44) est formé sur un côté du corps de base (26) le long duquel s'étend la conduite de dérivation (33), et en ce que la soupape de décharge (35) est agencée entre l'appendice (44) et un tronçon de conduite de pression (321) de la conduite de pression (32), dans lequel est agencée au moins une valve de sortie (31) pour assurer l'étanchéité de ladite au moins une chambre de pompe (29) par rapport à la conduite de pression (32).
  8. Pompe selon l'une des revendications précédentes, caractérisée en ce que la conduite de distribution (18) est orientée transversalement par rapport à la conduite de pression (32) et/ou la conduite de distribution (18) et la conduite de dérivation (33) définissent un deuxième plan de pompe orienté perpendiculairement au dit plan de pompe.
  9. Pompe selon l'une des revendications précédentes, caractérisée en ce que le premier tronçon d'appendice (45) présente un alésage axial (63) le long du premier axe (47), dans lequel est insérée une soupape de surpression (61), et en ce que l'alésage (63) est relié par l'intermédiaire d'un canal de surpression (67) à la conduite de pression (32).
  10. Pompe selon la revendication 9, caractérisée en ce que le canal de surpression (67) s'étend en tant que canal axial le long du premier axe (47) et/ou en ce que le canal de surpression (67) est relié à un tronçon de la conduite de pression (32), dans lequel est agencé le corps d'obturation de soupape (36) de la soupape de décharge (35), et duquel est dérivée la conduite de dérivation (33).
  11. Pompe selon l'une des revendications 1 à 8, caractérisée en ce que le deuxième tronçon d'appendice (46) présente un alésage axial (51) le long du deuxième axe (48), dans lequel est inséré un poussoir de commutation (53), et en ce que l'alésage (51) est relié par l'intermédiaire d'un canal de commutation (56) à la chambre de pression (40), le poussoir de commutation (53) étant mobile axialement, en fonction de la pression dans la chambre de pression (40), d'une première position de commutation à une deuxième position de commutation et inversement, pour actionner un élément de commutation électrique (55).
  12. Pompe selon la revendication 11, caractérisée en ce que le canal de commutation (56) s'étend en tant que canal axial le long du deuxième axe (48).
  13. Pompe selon la revendication 11 ou la revendication 12, caractérisée en ce que l'alésage axial (51) est relié à la conduite de pression (32) via un canal de compensation (57), par l'intermédiaire duquel le poussoir de commutation (53) est sollicité sur une surface active (59) avec une pression du liquide dans la conduite de pression (32), cette surface active (59) agissant à l'encontre d'une surface active (58) du poussoir de commutation (53) par l'intermédiaire de laquelle le poussoir de commutation (53) est sollicité avec une pression du liquide dans la chambre de pression (40).
  14. Pompe selon la revendication 13, caractérisée en ce que le canal de compensation (57) s'étend le long du premier axe (47) ou parallèlement à celui-ci.
  15. Pompe selon l'une des revendications 11 à 14, caractérisée en ce que la pompe (14) présente un module, qui comprend le poussoir de commutation (53) et l'élément de commutation électrique (55), et se présente sous la forme d'un commutateur manométrique (25) inséré dans l'alésage (51).
  16. Pompe selon l'une des revendications précédentes, caractérisée en ce que la pompe (14) est une pompe à vilebrequin.
  17. Appareil de nettoyage haute-pression comprenant au moins une pompe (14) selon l'une des revendications précédentes.
EP12705138.1A 2012-02-20 2012-02-20 Pompe pour un nettoyeur haute pression et un nettoyeur haute pression Active EP2817516B1 (fr)

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CN106662086B (zh) * 2014-07-30 2019-09-13 阿尔弗雷德·卡赫欧洲两合公司 活塞泵与具有这种活塞泵的高压清洁设备
CN106466676A (zh) * 2015-08-20 2017-03-01 河南省银河通信电器设备有限公司 一种野战高压清洗装置
CN105435986A (zh) * 2015-12-19 2016-03-30 台州市正茂动力工具有限公司 一种高压清洗机关枪停机装置
CN106314824A (zh) * 2016-09-12 2017-01-11 中国人民解放军海军航空工程学院青岛校区 一种多功能飞机清洗设备
DE102017206504A1 (de) * 2017-04-18 2018-10-18 Robert Bosch Gmbh Druckreinigungsvorrichtung mit einer Druckerzeugungseinheit
EP3645179B1 (fr) * 2017-06-29 2022-09-07 Alfred Kärcher SE & Co. KG Appareil de nettoyage haute pression
DE102020131798A1 (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
DE3936155C2 (de) * 1989-10-31 1995-04-13 Kraenzle Josef Vorrichtung zur Steuerung von Pumpen für Flüssigkeitsförderanlagen
DE4404925A1 (de) * 1994-02-16 1995-08-17 Kaercher Gmbh & Co Alfred Hochdruckreinigungsgerät
DE202005021232U1 (de) * 2005-10-11 2007-05-31 Alfred Kärcher Gmbh & Co. Kg Hochdruckreinigungsgerät
DE102007003521B4 (de) * 2007-01-18 2011-06-09 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät

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WO2013123969A1 (fr) 2013-08-29
DK2817516T3 (en) 2016-08-01

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