WO2013107519A1 - Pompe à pistons pour appareil de nettoyage à haute pression - Google Patents

Pompe à pistons pour appareil de nettoyage à haute pression Download PDF

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Publication number
WO2013107519A1
WO2013107519A1 PCT/EP2012/050867 EP2012050867W WO2013107519A1 WO 2013107519 A1 WO2013107519 A1 WO 2013107519A1 EP 2012050867 W EP2012050867 W EP 2012050867W WO 2013107519 A1 WO2013107519 A1 WO 2013107519A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
piston pump
support
pump
support plate
Prior art date
Application number
PCT/EP2012/050867
Other languages
German (de)
English (en)
Inventor
Robert Nathan
Original Assignee
Alfred Kärcher Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alfred Kärcher Gmbh & Co. Kg filed Critical Alfred Kärcher Gmbh & Co. Kg
Priority to PCT/EP2012/050867 priority Critical patent/WO2013107519A1/fr
Priority to CN201280062667.3A priority patent/CN103998778B/zh
Priority to EP12702458.6A priority patent/EP2805051B1/fr
Priority to BR112014012998A priority patent/BR112014012998A2/pt
Publication of WO2013107519A1 publication Critical patent/WO2013107519A1/fr
Priority to US14/334,068 priority patent/US20140328698A1/en

Links

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
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • 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
    • F04B53/02—Packing the free space between cylinders and pistons
    • 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
    • F04B1/14—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 having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/143—Cylinders
    • 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
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes

Definitions

  • the invention relates to a piston pump for a high-pressure cleaning device, with a plurality of pump chambers, in each of which a reciprocable piston dips and which are in each case via a suction valve with a suction inlet and a pressure valve with a pressure outlet in flow communication, wherein the piston in each case by a sealing ring are surrounded, which is supported in the radial direction by an annular wall and in the axial direction of a support ring.
  • a liquid preferably water
  • the pistons can be driven to a reciprocating motion, for example by means of a swash plate, so that the volumes of the pumping chambers change periodically and sucked liquid from the suction inlet via the suction valves in the pumping chambers, there pressurized and discharged through the pressure valves and the pressure outlet can be.
  • a pressure hose can be connected, which carries at its free end a delivery member for the pressurized liquid, for example a spray nozzle or a spray lance.
  • the pump chambers are each sealed by means of a sealing ring which surrounds the piston immersed in the pump chamber in the circumferential direction.
  • the sealing ring may for example form a sealing lip which is pressed under the pressure prevailing in the pump chamber pressure against the lateral surface of the piston.
  • a support ring In the radial direction of the sealing ring is usually supported by an annular wall and for support in the axial direction is usually a support ring is used.
  • Such piston pumps are known for example from DE 44 45 519 Cl.
  • the liquid in the pump chambers is pressurized to over 100 bar.
  • the piston pump is therefore subject during its operation considerable mechanical loads and must have a high mechanical strength. Therefore, the piston pumps usually have a considerable material thickness. This is associated with not inconsiderable manufacturing costs.
  • the relatively high material strength has the consequence that the housing of the piston pump, which is usually produced in a casting process, during manufacture undergoes a long cooling process, which limits the production rate of the housing. This also increases the manufacturing cost of the piston pump
  • Object of the present invention is to develop a piston pump of the type mentioned in such a way that it can be produced more cheaply.
  • a piston pump of the generic type according to the invention in that it comprises a one-piece support plate, which forms the support rings and surrounding the annular walls in the circumferential direction.
  • All support rings which support the sealing rings each surrounding a piston in the circumferential direction in the axial direction, are integrated in the piston pump according to the invention in a one-piece support shield. This allows a simpler installation of the piston pump, since all support rings can be positioned in a single assembly step.
  • the present invention used for use one-piece support plate also has the function of the above-mentioned ring walls in
  • the support plate on a plurality of support sleeves, in each of which an annular wall is immersed.
  • the sealing of the pumping spaces by means of the sealing rings which each surround a piston and in turn are surrounded by an annular wall and are supported on a support ring in the axial direction.
  • the piston pump according to the invention comprises three pistons, each immersed in a pump chamber, each pump chamber having an annular wall which supports a sealing ring in the radial direction and which dips into a support sleeve of the support plate.
  • the annular wall may be formed particularly thin-walled in such a configuration and yet the liquid to be delivered can be placed in the pump chambers under a high pressure.
  • the piston pump comprises a pump block, which has the pumping chambers and which is integrally connected to the support plate. This makes it possible to additionally reduce the manufacturing costs and also to simplify the assembly of the piston pump.
  • an adhesive bond can be used as an integral connection.
  • An adhesive layer may be provided, for example, between the respective annular walls surrounding a respective sealing ring in the circumferential direction and the support plate surrounding the annular wall in the circumferential direction. This allows a mechanically strong connection between the pump block and the support plate.
  • the adhesive layer can also serve as a sealing element for the liquid to be delivered.
  • a uniform stress distribution and power transmission can be achieved. Voltage peaks, which can often occur with a screw connection, can be reduced.
  • the pump block is welded to the support plate. This allows a particularly strong connection that can withstand very high pressures reliably.
  • each of a sealing ring in the circumferential direction surrounding ring walls are each welded to a surrounding support sleeve.
  • the pump block and the support plate are made of a plastic material.
  • the support plate comprises support sleeves, as has been explained above, the support sleeves can each be placed on an annular wall and welded thereto in a structurally simple manner.
  • the welded joint allows a permanent fixation of the two parts to each other, so that they can then perform no relative movement more. As with the weld joint and an optimal seal can be achieved, additional seals between the two parts can be omitted.
  • the support plate is seated on a guide plate having guide members for guiding the piston in the axial direction.
  • the pistons can be guided in the axial direction.
  • the guide plate has the function to support the support plate in the axial direction.
  • the support plate preferably has coaxial with the support sleeves aligned support collar which sit on the guide plate and each surrounding a piston in the circumferential direction.
  • the support shield can be designed in a constructive way. Support the way on the guide plate.
  • the use of the support collar has the advantage that the mechanical strength of the support plate is increased, the material thickness of the support plate can be kept relatively low.
  • the support collars preferably each have a drainage opening, for example a drainage slot. Via the drainage opening, liquid which inadvertently emerges from the pump chambers via the sealing ring surrounding a respective piston can be released to the environment.
  • a particularly high mechanical strength with relatively low use of material is achieved in a particularly preferred embodiment of the invention in that the support plate is supported by a convex guide plate which forms a lid for a swash plate housing.
  • the support plate in the axial direction supporting guide plate is convex. This gives him a particularly high mechanical strength and allows to reduce the material strength of the guide plate.
  • the guide plate in such an embodiment performs the function of a cover for the swash plate housing, in which a swash plate is arranged, with which the pistons to achieve a reciprocating Cooperation together.
  • the swashplate can be rotated about the longitudinal axis of the piston pump, and the swirling motion of the swashplate allows the pistons to be driven to reciprocate, under the action of which the volumes of the pumping chambers are periodically changed.
  • Figure 1 is a schematic longitudinal sectional view of an advantageous embodiment of a piston pump according to the invention
  • Figure 2 is a plan view of a welded to a support plate pump block of the piston pump of Figure 1;
  • Figure 3 is a sectional view of the welded to the support plate pump block along the line 3-3 in Figure 2 and
  • Figure 4 a sectional view of the pump block and the support plate in the manner of an exploded view.
  • the piston pump 10 comprises a pump head 12 with a suction inlet 14, via which the piston pump 10 can be supplied with a liquid to be pressurized, preferably water.
  • a supply line can be connected to the suction inlet 14.
  • the pump head 12 also has a pressure outlet 16 through which the pressurized fluid can be dispensed.
  • a pressure hose can be connected, which carries at its free end a delivery member for the pressurized liquid, for example a spray lance or a spray nozzle.
  • the pump head 12 is mounted in the axial direction with respect to a pump longitudinal axis 18 on a pump block 20 having a plurality of pump chambers 22, in each of which a piston 24 is immersed.
  • the piston pump 10 shown in the drawing has a total of three pump chambers, wherein in the drawing only one pump chamber 22 can be seen.
  • the pump chambers are arranged distributed uniformly around the pump longitudinal axis 18 and each have the same radial distance to the pump longitudinal axis 18.
  • the pump chambers 22 are in each case via a suction valve 26 to the suction inlet 14 and via a pressure valve 28 with a central pressure chamber 30 in flow communication, which form the pump head 12 and the pump block 20 between them.
  • the pressure chamber 30 is adjoined in the axial direction by a pressure line 32 which is aligned coaxially to the pump longitudinal axis 18 and via which the pressure chamber 30 is in flow communication with the pressure outlet 16.
  • a central, rotationally symmetrical to the pump longitudinal axis 18 formed insert member 34 is held, which is formed in the manner of a piston and surrounded by two sealing rings which are disposed between the insert member 34 and the wall of the pressure chamber 30.
  • the insert part 34 forms a holding element for closing springs 40 of the pressure valves 28.
  • the insert part 34 On its front side facing away from the closing springs 40, the insert part 34 has a recess 42 into which a closing body 44 of a central non-return valve dips, by means of which a central passage of the insert valve 34 can be closed.
  • the sealing of the pumping spaces 22 in the direction away from the pump head 12 takes place in each case with the aid of a sealing ring 46, which has a sealing lip 48 and surrounds a piston 24 in the circumferential direction.
  • the sealing ring 46 is surrounded by a collar-like annular wall 50 of the pump block 20 in the circumferential direction.
  • the annular wall 50 is cylindrical and aligned coaxially with a piston longitudinal axis 52. Relative to the piston longitudinal axis 52, the annular wall 50 supports the sealing ring 46 radially.
  • a one-piece support plate 54 On the pump head 12 side facing away from the pump block 20 is followed by a one-piece support plate 54, the configuration of which results in particular from Figure 4. It has support rings 56 which each support a sealing ring 46 in the axial direction. Each support ring 56 is followed by a cylindrical support sleeve 58, which is aligned coaxially with a piston longitudinal axis 52 and surrounds an annular wall 50 in the circumferential direction.
  • On the back of the support plates 54 facing away from the support plate 54 carries a plurality of cylindrical support collar 60, which is also coaxial with the piston longitudinal axes 52 are aligned and each having a drainage opening in the form of a drainage slot 62.
  • the support plate 54 is integrally formed and made of a plastic material. Also for the production of the pump head 12 and the pump block 20 is in each case a plastic material used. In the area of the annular walls 50 and the surrounding support sleeves 58 of the pump block 20 is welded to the support plate 54. Each annular wall 50 is thus integrally connected via a circumferential weld with a support sleeve 58 into which the annular wall 50 is immersed. This gives the ring walls 50 a high mechanical stability, without having to have a considerable material thickness.
  • the support plate 54 With the support collar 60, the support plate 54 is supported in the axial direction on a guide plate 64 having a plurality of guide members in the form of coaxially aligned with the piston longitudinal axes 52 guide sleeves 66. At each guide sleeve 66 is a piston 24 slidably. By means of the guide sleeves 66 each surrounding return spring 68, the pistons are pressed against a swash plate 70 which is rotatably mounted about the pump axis 18 in a swash plate housing 72.
  • the guide plate 54 forms a convexly outwardly curved cover for the swash plate housing 72, on which the guide plate 64 is supported in the axial direction.
  • the swash plate 70 can be rotated in the usual manner by a known per se and therefore not shown in the drawing drive motor, in particular an electric motor to the pump axis 18, wherein the rotational movement of the motor shaft via a schematically illustrated in Figure 1 gear 74 on the Swash plate 70 is transmitted.
  • each of a piston 24 circumferentially surrounding sealing rings 46 are fixed reliably both in the axial direction and in the radial direction, so that by means of the sealing rings 46 a high tightness can be achieved even at high pressures. Nevertheless, liquid exiting from the pump chambers 22 can escape to the outside via the drainage slots 62.
  • the guide plate 64 can be placed on the swash plate housing 72 after the swash plate 70 has been mounted, wherein previously the pistons 24 were inserted into the guide sleeves 66.
  • the support plate 54 can be placed on the guide plate 64, after previously the suction valves 26 were mounted in the pump block 20 and the pump block 20 has been welded to the support plate 54.
  • the ring walls 50 are each welded to a support sleeve 58.
  • an ultrasonic welding can be used, since both the pump block 20 and the support plate 54 are made of a plastic material.
  • the pump head 12 After inserting the pressure valves 28 and the central insert member 34 including the central closure member 44 in the pump block 20 can be placed in a subsequent assembly step, the pump head 12 in the axial direction of the pump block 20, wherein between the pump head 12 and the pump block 20, an elastically deformable sealing ring 76 is positioned.
  • the pump head 12 can then be clamped to the pump block 20.
  • a clamping element 77 can be used, which is shown only schematically in FIG. 1 and engages the end face 78 of the pump head 12 facing away from the pump block 20.
  • the clamping element 77 can engage over the pump head 12, the pump block 20 and the support plate 54 and can be screwed with radially outwardly pointing screw receptacles of the guide plate 64.
  • the manufacture and assembly of the piston pump 10 is thus very simple.
  • the use of the one-piece support plate 54 with the support sleeves 60 surrounding a respective annular wall 20 and the support collar 60 aligned coaxially with the support sleeves 58 makes it possible to minimize the material usage of the support shield 54 and also the material usage of the pump block 20 in the area of the annular walls 50.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Pompe à pistons (10) pour un appareil de nettoyage à haute pression, comportant plusieurs cavités (22) dans chacune desquelles pénètre un piston (24) effectuant un mouvement de va-et-vient et qui se trouvent chacune en communication d'écoulement avec un orifice d'aspiration (14) par l'intermédiaire d'une soupape d'aspiration (26) et avec un orifice de refoulement (16) par l'intermédiaire d'une soupape de refoulement (28), les pistons (24) étant chacun entourés par une bague d'étanchéité (46) qui s'appuie dans la direction radiale sur une paroi annulaire (50) et dans la direction axiale sur une bague de support (56). L'objet de la présente invention est de perfectionner ladite pompe à pistons de manière qu'elle telle qu'elle soit moins onéreuse à fabriquer et à monter. A cet effet, ladite pompe à pistons (10) comporte une structure de support (54) en une seule pièce qui forme les bagues de support (56) et qui entoure les parois annulaires (50) dans la direction périphérique.
PCT/EP2012/050867 2012-01-20 2012-01-20 Pompe à pistons pour appareil de nettoyage à haute pression WO2013107519A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/EP2012/050867 WO2013107519A1 (fr) 2012-01-20 2012-01-20 Pompe à pistons pour appareil de nettoyage à haute pression
CN201280062667.3A CN103998778B (zh) 2012-01-20 2012-01-20 用于高压清洁设备的活塞泵
EP12702458.6A EP2805051B1 (fr) 2012-01-20 2012-01-20 Pompe à pistons pour appareil de nettoyage à haute pression
BR112014012998A BR112014012998A2 (pt) 2012-01-20 2012-01-20 bomba de pistão para um aparelho de limpeza de alta pressão
US14/334,068 US20140328698A1 (en) 2012-01-20 2014-07-17 Piston pump for a high-pressure cleaning appliance

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2012/050867 WO2013107519A1 (fr) 2012-01-20 2012-01-20 Pompe à pistons pour appareil de nettoyage à haute pression

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US14/334,068 Continuation US20140328698A1 (en) 2012-01-20 2014-07-17 Piston pump for a high-pressure cleaning appliance

Publications (1)

Publication Number Publication Date
WO2013107519A1 true WO2013107519A1 (fr) 2013-07-25

Family

ID=45562982

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/050867 WO2013107519A1 (fr) 2012-01-20 2012-01-20 Pompe à pistons pour appareil de nettoyage à haute pression

Country Status (5)

Country Link
US (1) US20140328698A1 (fr)
EP (1) EP2805051B1 (fr)
CN (1) CN103998778B (fr)
BR (1) BR112014012998A2 (fr)
WO (1) WO2013107519A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022100388A1 (de) 2022-01-10 2023-07-13 Alfred Kärcher SE & Co. KG Motorpumpeneinheit, insbesondere für ein Hochdruckreinigungsgerät

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2146709A (en) * 1935-07-10 1939-02-14 Union Steam Pump Company Pump for viscolizer valves
US3323461A (en) * 1965-01-21 1967-06-06 Richard A Bennett Metering pump
DE4445519C1 (de) 1994-12-20 1996-06-05 Kaercher Gmbh & Co Alfred Kolbenpumpe für ein Hochdruckreinigungsgerät
US6092998A (en) * 1998-03-20 2000-07-25 Devilbiss Air Power Company Pump for a pressure washer
US20110027106A1 (en) * 2008-07-30 2011-02-03 Maruyama Mfg Co., Inc. Reciprocating pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3362343A (en) * 1966-03-01 1968-01-09 Clamar Inc Liquid dispenser
DE3623421A1 (de) * 1986-07-11 1988-01-14 Vickers Systems Gmbh Lenkhilfpumpe
CN1089868C (zh) * 1996-09-19 2002-08-28 罗伯特·博施有限公司 活塞泵
CN2408258Y (zh) * 2000-02-03 2000-11-29 朱敬之 潜水泵
EP1435457A1 (fr) * 2003-01-03 2004-07-07 Lavorwash S.p.A. Pompe axiale avec dispositif automatique de réglage du débit
DE102007020299A1 (de) * 2007-04-20 2008-10-23 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
DE102007020298A1 (de) * 2007-04-20 2008-10-23 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2146709A (en) * 1935-07-10 1939-02-14 Union Steam Pump Company Pump for viscolizer valves
US3323461A (en) * 1965-01-21 1967-06-06 Richard A Bennett Metering pump
DE4445519C1 (de) 1994-12-20 1996-06-05 Kaercher Gmbh & Co Alfred Kolbenpumpe für ein Hochdruckreinigungsgerät
US6092998A (en) * 1998-03-20 2000-07-25 Devilbiss Air Power Company Pump for a pressure washer
US20110027106A1 (en) * 2008-07-30 2011-02-03 Maruyama Mfg Co., Inc. Reciprocating pump

Also Published As

Publication number Publication date
EP2805051A1 (fr) 2014-11-26
BR112014012998A2 (pt) 2017-06-13
EP2805051B1 (fr) 2019-12-11
CN103998778B (zh) 2017-05-31
CN103998778A (zh) 2014-08-20
US20140328698A1 (en) 2014-11-06

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