EP2766603B1 - Kolbenpumpe für ein hochdruckreinigungsgerät - Google Patents

Kolbenpumpe für ein hochdruckreinigungsgerät Download PDF

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Publication number
EP2766603B1
EP2766603B1 EP12769117.8A EP12769117A EP2766603B1 EP 2766603 B1 EP2766603 B1 EP 2766603B1 EP 12769117 A EP12769117 A EP 12769117A EP 2766603 B1 EP2766603 B1 EP 2766603B1
Authority
EP
European Patent Office
Prior art keywords
piston
supporting wall
piston pump
pump according
support wall
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
EP12769117.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2766603A1 (de
Inventor
Thomas Hofer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alfred Kaercher SE and Co KG
Original Assignee
Alfred Kaercher SE and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alfred Kaercher SE and Co KG filed Critical Alfred Kaercher SE and Co KG
Publication of EP2766603A1 publication Critical patent/EP2766603A1/de
Application granted granted Critical
Publication of EP2766603B1 publication Critical patent/EP2766603B1/de
Active legal-status Critical Current
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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
    • 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
    • F04B1/145—Housings
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block

Definitions

  • the invention relates to a piston pump for a high-pressure cleaning device, with a plurality of reciprocable pistons, each immersed in a pump chamber and slidably supported on a piston guide member, wherein the piston guide member has a support wall, are arranged on the plurality of guide elements, each leading a piston ,
  • Such piston pumps are for example off DE 39 18 022 C2 known.
  • a liquid preferably water
  • the pump chamber is connected via a suction valve with a suction line for sucking liquid and a pressure valve with a pressure line for discharging pressurized liquid.
  • An accessory device can be connected to the pressure line, for example a high-pressure hose which carries a dispensing device at its free end, in particular a spray lance or a spray nozzle.
  • the pistons are reciprocally moved so that the volumes of the pumping chambers periodically change to aspirate, pressurize and dispense the liquid.
  • the pistons are slidably held on a piston guide member having a support wall and a plurality of guide elements.
  • the guide elements each guide a piston.
  • the support wall in many cases forms a lid which is placed on the housing of a drive mechanism, for example on the housing a swashplate against which the pistons abut and which is rotated by a motor.
  • the piston guide part is exposed to high mechanical loads. It therefore usually has reinforcing ribs and a considerable material thickness. This leads to increased manufacturing costs 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 is cheaper to produce.
  • a piston guide member with a curved support wall is used. Due to the curvature of the support wall on the one hand, the mechanical strength of the piston guide member can be considerably increased, without the support wall must have reinforcing ribs or a large material thickness. On the other hand, the curved surface of the supporting wall enlarges its surface, so that it also has an improved thermal load capacity, since due to the larger surface a reliable heat dissipation is ensured without the necessity of providing cooling fins for the supporting wall. The relatively small amount of material required for the support wall reduces the weight of the piston guide member. In addition, the piston guide member with the curved support wall can be produced inexpensively, so that the manufacturing cost of the piston pump can be reduced.
  • the supporting wall is curved in the same direction on its front side facing the pumping chambers and on its rear side facing away from the pumping chambers.
  • the support wall thereby forms a cavity or depression, which gives the support wall a particularly high mechanical strength.
  • the support wall is curved in the manner of a spherical cap. It can for example form a spherical cap of a housing, which receives a drive mechanism for the piston.
  • the supporting wall is curved in the direction facing the pumping chambers or in the direction away from the pumping chambers. This has the advantage that its central region is axially offset from its outer periphery.
  • the guide elements are integrally connected to the support wall and are on the side facing away from the pump chambers of the support wall from the support wall.
  • the support wall is curved in the direction of the pump chambers, so that it forms on its side facing away from the pump chambers a recess or cavity into which immerse the guide elements.
  • the support wall may for example form a lid for a swash plate housing, wherein the lid is curved outward or immersed in the housing.
  • the guide elements have a base which is integrally connected to the support wall and projects at least on one side of the support wall. It is advantageous if the base protrudes from the support wall on both sides of the support wall.
  • radially increasing reinforcing ribs are integrally formed on the outer sides of the guide elements to increase the mechanical and thermal load capacity of the piston guide part.
  • the guide elements have a base which protrudes from the support wall on the side of the support wall facing the pump chambers and bears radially projecting reinforcing ribs on its outer side. Due to the use of the reinforcing ribs, the material used for the base can be kept low, without their mechanical or thermal capacity is impaired. It is particularly advantageous if the reinforcing ribs protrude in the axial direction over the base. With its axially projecting portion, the reinforcing ribs define a receiving space for an annular member of the piston pump which circumferentially surrounds the piston passing through the guide member. This may be, for example, a guide ring or a sealing ring.
  • the reinforcing ribs not only have the purpose in such a configuration to increase the mechanical and thermal stability of the base, but also serve to define an annular member which surrounds a piston in the circumferential direction.
  • the guide elements have an integrally connected to the supporting wall base, to which a guide sleeve connects in the axial direction, which surrounds a piston in a form-fitting manner in the circumferential direction.
  • the base can have a higher material thickness than the guide sleeve.
  • the outer side of the base merges via an inwardly directed, preferably radially aligned step into the outer side of the guide sleeve.
  • a particularly high mechanical stability is achieved in a preferred embodiment of the invention in that on the outer circumference of the support wall, a cylindrical collar is formed.
  • the cylindrical collar immersed in a preferred embodiment in a cylindrical housing of a swash plate.
  • FIGS. 1 to 4 is schematically illustrated a first embodiment of a piston pump according to the invention, which is generally occupied by the reference numeral 10. It can be placed in a conventional manner on a motor, not shown in the drawing, which rotatably drives a swash plate 12 which is rotatably mounted in a swash plate housing 14 by means of a ball bearing 16.
  • the piston pump 10 comprises a plurality of identically designed pistons 18, which bear against the front side of the swash plate 12 facing away from the ball bearing 16 and with the aid of return springs 20 in the direction pressed on the swash plate 12.
  • the pistons 18 are held linearly displaceable on a piston guide part 22 of the piston pump 10.
  • the piston guide member 22 has for this purpose guide elements 24 which each guide a piston 18 and which are integrally connected to a support wall 26 of the piston guide member 22.
  • the support wall 26 is configured in the manner of a spherical cap and in the in the FIGS. 1 to 4 embodiment shown curved in the swash plate 12 facing away from the direction. It forms a lid which is placed on a cylindrical jacket 28 of the swash plate housing 14. On the outer circumference of the support wall 26, a cylindrical collar 30 is formed, which dips into the jacket 28 of the swash plate housing 14 with the interposition of a sealing element 32.
  • the guide elements 24 are formed identically and each comprise an integrally connected to the support wall 26 cylindrical base 34 which protrudes both on the swash plate 12 remote from the front side 36 of the support wall 26 and on the swash plate 12 facing back 38 of the support wall 26 of the support wall , In the direction of the swash plate 12, a guide sleeve 40 integrally connects to the base 34, which surrounds the respective piston 18 in a form-fitting manner.
  • the material thickness of the base 34 is chosen to be greater than the material thickness of the guide sleeve 40th
  • the formed on the back 38 of the support wall 26 to the base 34 guide sleeves 40 have, in contrast to the sockets 34 on the outside no reinforcing ribs.
  • a pump block 46 of the piston pump 10 is placed and on the pump block 46, a pump head 48 of the piston pump 10 is placed.
  • a pump block 46 of the piston pump 10 is placed and on the pump block 46, a pump head 48 of the piston pump 10 is placed.
  • the pump block 46 has pump chambers 52 into each of which a piston 18 is immersed and which are in fluid communication with a suction line 56 via an inlet opening 54 and with an outlet opening 58 with a pressure line 60. Between the pump chambers 52 and the suction line 56 is a not shown in the drawing, known per se suction valve is arranged, and between the pump chambers 52 and the pressure line 60 is a not shown in the drawing, known per se pressure valve is arranged.
  • the suction line 56 connects the pump chambers 52 with a suction inlet 62 of the piston pump 10, to which, for example, a suction hose can be connected.
  • the pressure line 60 connects the pump chambers 52 with a Pressure outlet 64 of the piston pump 10 to which, for example, a pressure hose can be connected.
  • the pistons 18 When the swashplate 12 is rotated about its axis of rotation 66, the pistons 18 perform a reciprocating motion parallel to the axis of rotation 66, periodically changing the volume of the respective pumping chamber 52 into which they are immersed so that liquid passes through the suction inlet 62 and the suction line 56 sucked into the pump chamber 52, then pressurized and then discharged via the pressure line 60 and the pressure outlet 64.
  • the pistons 18 are in the axial direction by means of the piston guide member 22, d. H. guided parallel to the axis of rotation 66.
  • the pistons 18 each slide along a guide sleeve 40, which is connected in one piece with the support wall 26 via a base 34.
  • the latter has a high mechanical stability due to its spherical cap-shaped configuration, which is reinforced by the cylindrical concentric with the axis of rotation 66 aligned collar 30 which is integrally connected to the support wall 26.
  • the support wall 26 is characterized by a high thermal stability, since it has a relatively large surface over which heat can be dissipated.
  • FIGS. 5 to 8 a second advantageous embodiment of a piston pump according to the invention is shown, which is generally occupied by the reference numeral 70.
  • the piston pump 70 is configured similarly to the above-described piston pump 10.
  • the piston pump 70 is driven by a swash plate 72 which is rotatably mounted in a swash plate housing 74 and is rotated by a motor, not shown in the drawing.
  • the piston guide part 82 comprises guide elements 84, which are integrally connected to a support wall 86 of the piston guide part 82.
  • the support wall 86 is placed on a jacket 88 of the swash plate housing 74 and on the outer periphery of the support wall 86, a cylindrical collar 90 is formed, which surrounds an end portion of the jacket 88 in the circumferential direction.
  • support wall 26 of the piston pump 10 and the support wall 86 of the piston pump 70 is designed in the manner of a spherical cap.
  • the support wall 86 is arched in the direction of the swash plate 72 facing direction.
  • the support wall 86 thus forms on its front side 96 facing away from the swash plate 72 a depression or cavity and with its swash plate 72 facing the rear side 98 in the swash plate housing 74 a.
  • the guide elements 84 of the piston pump 70 each comprise a cylindrical base 94, which is integrally formed on the support wall 86 and protrudes on both the front side 96 and on the rear side 98 via the support wall 86. Facing the swash plate 72 closes integrally to the base 94, a guide sleeve 100 whose material thickness is selected to be lower than the material thickness of the cylindrical base 94.
  • the outer side of the cylindrical base 94 passes through a radially inwardly directed step 102 in the Outside of the guide sleeve 100 via. This is especially true FIG. 8 clear.
  • the cylindrical base 94 has reinforcing ribs 104 on the outside only in its region projecting beyond the front side 96, whereas the region of the cylindrical base 94 projecting beyond the rear side 98 bears no reinforcing ribs on the outside. Instead, 100 further reinforcing ribs 105 are formed on the outside of the guide sleeves, which make it possible to keep the material thickness of the guide sleeves 100 low without thereby affecting the mechanical or thermal stability of the guide sleeves 100.
  • the piston pump 70 comprises a pump block 106, which is placed on the piston guide part 82, and a pump head 108, which is placed on the pump block 106.
  • a pump block 106 which is placed on the piston guide part 82
  • a pump head 108 which is placed on the pump block 106.
  • the pump block 106 has pump chambers 112, in each of which a piston 78 is immersed and which are in fluid communication via an inlet opening 114 with a suction line 116 and via an outlet opening 118 with a pressure line 120. Via the suction line 116, the pump chambers 112 are connected to a suction inlet 122 and via the pressure line 120, the pump chambers 112 are connected to a pressure outlet 124. Between the pumping chambers 112 and the suction line 116 is a not shown in the drawing, the expert known per se suction valve, and arranged between the pump chambers 112 and the pressure line 120 is in each case arranged in the drawing, not shown in the drawing, known in the art per se pressure valve.
  • the pistons 78 are reciprocally moved so that the volume of the respective pumping chamber 112 into which the pistons 78 dip periodically changes to aspirate, pressurize and dispense liquid.
  • the pistons are in the axial direction, d. H. parallel to the axis of rotation 126 each guided by a guide sleeve 100 which is integrally connected via a cylindrical base 94 with the support wall 86. Due to its curved configuration, the support wall 86 has a high mechanical and thermal stability. The mechanical stability is additionally reinforced by the integrally formed on the support wall 86, concentric with the axis of rotation 126 aligned collar 90.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Cleaning By Liquid Or Steam (AREA)
EP12769117.8A 2011-10-12 2012-10-08 Kolbenpumpe für ein hochdruckreinigungsgerät Active EP2766603B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011054442A DE102011054442A1 (de) 2011-10-12 2011-10-12 Kolbenpumpe für ein Hochdruckreinigungsgerät
PCT/EP2012/069867 WO2013053670A1 (de) 2011-10-12 2012-10-08 Kolbenpumpe für ein hochdruckreinigungsgerät

Publications (2)

Publication Number Publication Date
EP2766603A1 EP2766603A1 (de) 2014-08-20
EP2766603B1 true EP2766603B1 (de) 2015-09-16

Family

ID=46980977

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12769117.8A Active EP2766603B1 (de) 2011-10-12 2012-10-08 Kolbenpumpe für ein hochdruckreinigungsgerät

Country Status (8)

Country Link
US (1) US9932971B2 (pt)
EP (1) EP2766603B1 (pt)
JP (1) JP5864764B2 (pt)
CN (1) CN103874854B (pt)
BR (1) BR112014007739A2 (pt)
DE (1) DE102011054442A1 (pt)
DK (1) DK2766603T3 (pt)
WO (1) WO2013053670A1 (pt)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
MX2018004665A (es) * 2017-04-17 2019-01-10 Fna Group Inc Bomba.
DE102022115745A1 (de) 2022-06-24 2024-01-04 Alfred Kärcher SE & Co. KG Taumelantrieb

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR744077A (pt) * 1933-04-10
US2374595A (en) * 1943-09-15 1945-04-24 Western Electric Co Reciprocable telescopic members
GB672173A (en) * 1949-08-06 1952-05-14 Siam Improvements in or relating to reciprocating pumps
GB1085511A (en) * 1964-07-09 1967-10-04 Lucas Industries Ltd Hydraulic reciprocating pumps
DE3347307A1 (de) * 1983-12-28 1985-07-11 Speck-Kolbenpumpen-Fabrik Otto Speck Kg, 8192 Geretsried Plungerpumpe
EP0324868A1 (de) * 1988-01-19 1989-07-26 Alfred Kärcher GmbH & Co. Kolbenpumpe für ein Hochdruckreinigungsgerät
DK165129C (da) 1988-09-02 1993-02-22 Westergaard Knud E Ind As Aksialstempelpumpe til vaesker, navnlig til brug i hoejtryksrenseapparater
DE8916257U1 (de) * 1988-09-02 1996-05-15 Kew Industri A/S, Hadsund Axialkolbenpumpe für Flüssigkeiten, besonders zur Verwendung bei Hochdruck-Reinigungsgeräten
DE3918022C2 (de) 1989-06-02 1994-07-14 Kaercher Gmbh & Co Alfred Axialkolbenpumpe für ein Hochdruckreinigungsgerät
DE9013630U1 (de) * 1990-09-28 1991-01-31 Speck-Kolbenpumpenfabrik Otto Speck GmbH & Co. KG, 8192 Geretsried Hochdruck-Flüssigkeitspumpe
NZ270736A (en) * 1995-03-17 1998-12-23 Noel Stephen Duke Wobble plate engine with pairs of rotating cylinders around output shaft, with port plates in end covers
DE29521522U1 (de) * 1995-06-23 1997-06-26 Alfred Kärcher GmbH & Co, 71364 Winnenden Motorpumpeneinheit für ein Hochdruckreinigungsgerät
IT1284106B1 (it) * 1996-07-04 1998-05-08 F A I P Srl Off Mec Flangia multifunzione specie per macchine idropulitrici
JP3476657B2 (ja) * 1997-06-05 2003-12-10 株式会社丸山製作所 プランジャポンプ及び多連プランジャポンプ装置
US6092998A (en) * 1998-03-20 2000-07-25 Devilbiss Air Power Company Pump for a pressure washer
EP1486674A1 (en) * 2003-06-11 2004-12-15 Hypro Corporation Variable displacement positive displacement pump
DE102004056019A1 (de) * 2004-11-16 2006-05-24 Alfred Kärcher Gmbh & Co. Kg Taumelantrieb
DE102005023449A1 (de) * 2005-05-20 2006-12-14 Schaeffler Kg Taumelscheibengetriebe
DE102005050009B4 (de) * 2005-10-11 2007-07-05 Alfred Kärcher Gmbh & Co. Kg Hochdruckreinigungsgerät
DE102007003521B4 (de) * 2007-01-18 2011-06-09 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
DE102007020299A1 (de) * 2007-04-20 2008-10-23 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
ITMI20090154U1 (it) * 2009-05-12 2010-11-13 Ipcleaning Spa Gruppo pompa perfezionato per macchime idropulitrici
CN201666235U (zh) * 2009-12-29 2010-12-08 颜志江 高压斜盘泵

Also Published As

Publication number Publication date
JP5864764B2 (ja) 2016-02-17
DE102011054442A1 (de) 2013-04-18
CN103874854B (zh) 2016-04-20
EP2766603A1 (de) 2014-08-20
DK2766603T3 (en) 2015-11-16
CN103874854A (zh) 2014-06-18
BR112014007739A2 (pt) 2017-04-04
WO2013053670A1 (de) 2013-04-18
US9932971B2 (en) 2018-04-03
US20140219832A1 (en) 2014-08-07
JP2014528550A (ja) 2014-10-27

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