WO2008128651A1 - Pompe à piston pour un appareil de nettoyage haute pression - Google Patents

Pompe à piston pour un appareil de nettoyage haute pression Download PDF

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Publication number
WO2008128651A1
WO2008128651A1 PCT/EP2008/002815 EP2008002815W WO2008128651A1 WO 2008128651 A1 WO2008128651 A1 WO 2008128651A1 EP 2008002815 W EP2008002815 W EP 2008002815W WO 2008128651 A1 WO2008128651 A1 WO 2008128651A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
sealing ring
chamber
pump according
piston pump
Prior art date
Application number
PCT/EP2008/002815
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 EP08735126A priority Critical patent/EP2140139A1/fr
Publication of WO2008128651A1 publication Critical patent/WO2008128651A1/fr

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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3216—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip supported in a direction parallel to the surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/3204—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip
    • F16J15/3228—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings with at least one lip formed by deforming a flat ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/56—Other sealings for reciprocating rods

Definitions

  • the invention relates to a piston pump for a high-pressure cleaner, with at least one pump chamber, in which a reciprocable piston dips and connected via a suction valve with a suction line for sucking liquid and a pressure valve with a pressure line for discharging pressurized liquid is, each piston is held axially movable in a piston chamber and surrounded by at least one sealing ring.
  • Such piston pumps are known for example from DE 198 01 146 Cl. With their help, a liquid, preferably water, sucked, placed under pressure and then discharged.
  • 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 spray nozzle.
  • the pistons are reciprocated, so that the volumes of the pumping chambers periodically change to aspirate, pressurize and discharge the liquid.
  • the pistons are each sealed by means of at least one sealing ring relative to the piston chamber.
  • the sealing ring is on the one hand on the periphery of the piston and on the other hand on the inner wall of the piston chamber sealingly.
  • usually sealing rings are used with two obliquely aligned sealing lips, wherein a radially inwardly disposed sealing lip rests on the outer circumference of the piston and a radially outer side arranged sealing lip on the wall of the piston chamber.
  • Object of the present invention is to develop a piston pump of the type mentioned in such a way that it can be manufactured and assembled cost.
  • Seal in the piston chamber is biased by a first support member in the direction of the pumping chamber.
  • the pistons are sealed by means of at least one sealing ring with respect to the wall of the piston chamber, wherein the sealing ring forms an annular bead, to which a sealing lip adjoins on the inside.
  • this sealing ring is biased in the piston chamber by a first support member in the direction of the pumping chamber.
  • the annular bead can be pressed against the wall of the piston chamber by the first support element and protruding inwards from the annular bead
  • Sealing lip is biased by the first support member in the direction of the pumping chamber, so that they can come to the plant sealingly on the outside of the piston. It has been shown that the gap between the piston and the Wall of the piston chamber can be reliably sealed by means of such a configured and biased sealing ring, wherein the sealing ring can be dimensioned considerably smaller than is the case with conventional sealing rings.
  • the smaller dimensioning of the at least one sealing ring in turn has the consequence that it must withstand lower pressure forces during operation of the piston pump, since the pressure forces of the size of the pressurized surface of the sealing ring are dependent.
  • the thus reduced application of force to the sealing ring makes it possible to fix it in a comparatively simple manner in the piston chamber.
  • a first support element is used, which may also be relatively small dimensions. The support element can be glued into the piston chamber without the need for additional fixing elements are used.
  • the piston pump according to the invention can therefore be manufactured and assembled inexpensively.
  • a further reduction of the assembly costs is achieved in an advantageous embodiment in that the sealing ring in the disassembled state, ie before its assembly, is symmetrical to a plane perpendicular to the longitudinal axis of the piston center plane.
  • the sealing ring thus has no preferred mounting direction and therefore does not have to be brought into a preferred position prior to insertion into the piston chamber.
  • the sealing ring is first pretensioned within the piston chamber by means of the first support element in the direction of the pumping chamber and thus brought into an asymmetrical shape with respect to the median plane. It has been found that this considerably reduces the assembly costs of the piston pump.
  • the sealing ring in the piston chamber is pressed between a first support surface and a second support surface independently of the piston.
  • the sealing ring can thus be fixed independently of the piston in the piston chamber, wherein it is subjected to a pressing force. An axial movement of the sealing ring is thus reliably prevented.
  • the sealing ring is pressed in the axial and in the radial direction between a first and a second support surface.
  • the sealing ring can be set in a structurally simple manner both in the axial direction and in the radial direction in the piston chamber, even before the piston is introduced into the piston chamber.
  • the first support surface is formed by a constriction of the piston chamber.
  • the constriction can be configured, for example, conical or arched or also form a step.
  • the second support surface is preferably formed by an end face of the first support element facing the pump space.
  • the sealing ring with its rear side facing away from the pump chamber, adjoins the end face of the first support element and is prestressed by it in the direction of the pumping chamber.
  • the first support element is formed by a support ring which surrounds the piston in the circumferential direction and which has a collar biasing the sealing ring in the direction of the pumping chamber.
  • the support ring has a main part surrounding the piston, which in an advantageous embodiment is radially inwardly on the piston and radially on the outside on the wall of the piston. chamber rests. From the main part of the support ring, a collar protrudes axially in the direction of the pumping chamber to the front. This collar acts on the sealing ring resting against the support ring with a bias in the direction of the pumping chamber.
  • the collar of the support ring acts on the sealing ring with a radially outwardly directed pressing force.
  • the sealing ring can thereby be pressed between the outside of the collar and the wall of the piston chamber.
  • the collar can apply an axially directed clamping force to a sealing lip which adjoins the annular bead radially on the inside, so that the sealing lip pointing radially inward in the disassembled state of the sealing ring is pushed out of a center plane aligned perpendicular to the longitudinal axis of the piston in the direction of the pumping chamber.
  • a piston guide is used, which is designed as a separate component and positioned between the piston pump and a pump drive.
  • the piston pump comprises a plurality of pistons, preferably three pistons, which are each held axially movably in a piston chamber and are thawed into a pump chamber. chen.
  • the separate piston guide must be aligned exactly with the pumping chambers to prevent the pistons from tilting.
  • the production of the pump chambers and the piston guide must be carried out with very low manufacturing tolerances and the assembly of the piston guide on the piston pump must be carried out very carefully.
  • the first support member has a first guide surface against which the piston is slidably engaged.
  • the first guide surface thus forms within the piston chamber a guide for the piston.
  • a common piston guide for all pistons of the piston pump can thus be dispensed with.
  • a separate piston guide is used with a first guide surface, which is provided by the force acting on the sealing ring with a biasing force in the direction of the pumping chamber first support member. The risk of jamming of the piston can be significantly reduced. In addition, this simplifies the assembly of the piston in the piston chamber.
  • the first support member is glued in a preferred embodiment in the piston chamber.
  • a second support element is arranged in the piston chamber, which axially supports a further sealing ring surrounding the piston in the circumferential direction.
  • the piston surrounded by at least two sealing rings.
  • a front sealing ring is configured as described above and can form a high-pressure seal, which seals the pumping chamber with respect to the piston chamber, so that the penetration of pressurized fluid into the piston chamber is prevented.
  • a rear sealing ring which is arranged at a greater distance from the pumping chamber than the front sealing ring, may be in the form of an oil seal, which prevents the rearward penetration of oil into the piston chamber.
  • the rear sealing ring may for example have a double lip.
  • the two sealing rings are each supported by a support element which is arranged in the piston chamber.
  • the second support element has a second guide surface against which the piston slidably bears.
  • the two support elements thus form a piston guide which reliably guides the piston in the axial direction and which is arranged in the piston chamber without having to use a separate piston guide in the form of an additional component.
  • a further simplification of the assembly of the piston pump is achieved in a preferred embodiment in that the two support elements form a preassembled unit which is inserted into the piston chamber.
  • the two support elements may be designed in the manner of a cartridge which can be inserted into the rear of the piston chamber and the two spaced-apart guide surfaces comprises, on which the piston is slidably applied. Due to its positioning within the piston chamber, the preassembled unit has virtually the same temperature as the region of the piston pump surrounding the respective pump chamber. This has the consequence that even during operation mechanical stresses, which could lead to jamming of the piston can be kept very low.
  • the preassembled unit is glued into the piston chamber.
  • Figure 1 a sectional view of a piston pump according to the invention
  • FIG. 2 shows an enlarged sectional view of a piston chamber of the piston pump from FIG. 1 without piston inserted;
  • FIG. 3 shows a sectional view of a sealing ring to be inserted into the piston chamber from FIG. 2 before its assembly and
  • FIG. 4 shows a sectional view of a preassembled insert which, instead of two separate support rings, can be inserted into the piston chamber of the piston pump from FIG.
  • FIG. 1 schematically shows a piston pump 10 according to the invention.
  • a piston pump 10 This can be placed in a customary manner on a pump drive, not shown in the drawing, known per se, which comprises a deworming disk against which a plurality of reciprocally movable pistons 12 of the piston pump 10 abut.
  • the pistons 12 each pass through a piston chamber 14 and dip into a pumping space 16.
  • the pump chambers 16 are in each case via a suction valve 18 with a suction line 20 in communication, via which a liquid, preferably water, can be sucked from a supply.
  • the pump chambers 16 are in each case via a pressure valve 22 and a common pumping chambers 16 common check valve 24 with a pressure line 26 in fluid communication, which opens into a control chamber 28.
  • a connecting line 30 Connected to the control chamber 28 in the flow direction of the pressurized liquid is a connecting line 30, which opens into an outlet line 34 formed by a pressure port 32, to which, for example, a high-pressure hose can be connected.
  • bypass line 36 connects the pressure line 26 with the suction line 20th
  • a control piston 40 is slidably held, which is integrally connected to an injector 42.
  • the injector 42 dips into the connecting line 30 and has in the usual way a cross-sectional constriction, from which a supply line 44 branches off via a transverse bore.
  • a supply line 44 and an adjoining this connecting piece 46 of the pressurized liquid can be added to a chemical.
  • the injector 42 is arranged on the end face of the control piston 40 facing away from the pressure line 26.
  • On its the pressure line 26 facing the rear of the control piston 40 carries a parallel to the injector 42 and offset arranged for this shift rod 48, which passes through a through hole 50 with its free end portion.
  • the shift rod 48 By means of the shift rod 48, a known per se and therefore not shown in the drawing switching device can be actuated by the shift rod 48 is moved.
  • the pump drive can be switched on and off.
  • the control piston 40 is frontally acted upon by the pressure prevailing in the supply line 44 and the pressure prevailing at the rear of the injector 42. In normal operation of the piston pump 10, the injector 42 is flowed through by pressurized liquid.
  • the cross-sectional constriction of the injector 42 leads to the generation of a negative pressure in the supply line 44 branching off from the injector 42.
  • the negative pressure is transmitted to the end face of the control piston 40, which is acted upon at the rear by the pressure prevailing upstream of the injector.
  • the thus acting on the control piston 40 pressure difference has the consequence that this occupies a forward position in which the coupled via the shift rod 48 to the control piston 40 switching device remains unactuated and thus the drive of the pump is not interrupted.
  • pressurized fluid interrupted, for example by closing a connected to the pressure line 26 via a high-pressure hose dispensing device, in particular a jet pipe or a spray lance, so builds on the first still working piston pump 10 in the pressure line 26 a very high pressure and at the same time prevents a flow through the injector 42, so that no dynamic pressure reduction occurs in this area. This results in the same pressure on both sides of the control piston 40.
  • a high-pressure hose dispensing device in particular a jet pipe or a spray lance
  • Supply line acted upon end face of the control piston 40 is selected to be greater than the acted upon by the pressure upstream of the injector 42 back of the control piston 40, the control piston 40 at identical Press pushed back so far that the switching device is actuated by the shift rod 48.
  • the drive of the piston pump 10 is turned off and a permanent high pressure load of the piston pump 10 is avoided.
  • a front sealing ring 54 is used, which is pressed in the axial direction between an arcuate constriction 56 of the piston chamber 14 and a first support member in the form of a front support ring 58 is.
  • the front support ring 58 comprises an annular main part 60 which rests against the outside of the wall of the piston chamber 14 and on its the pump chamber 16 facing end face 61 carries an axially in the direction of the pump chamber 16 projecting collar 62.
  • the radially outwardly directed outer side of the collar tapers in the axial direction and is arcuately curved.
  • the front sealing ring 54 is acted upon with a radially outwardly directed pressing force against the wall of the piston chamber 14.
  • the front sealing ring 54 is symmetrical to a perpendicular to the longitudinal axis 64 of the piston 12 aligned center plane 66.
  • the front sealing ring 54 therefore has no preferred mounting direction, ie the front of the sealing ring 54 is identically formed as the back. This facilitates the insertion of the front sealing ring 54 in the piston chamber 14 during assembly of the piston pump.
  • the front sealing ring 54 comprises an annular bead 68, to which a sealing lip 79 integrally connects radially inwardly.
  • the front sealing ring 54 forms a sealing disk whose material thickness can be less than 2 mm with a total diameter of more than 15 mm.
  • the material thickness of the front sealing ring 54 in the region of the annular bead 58 is about 1.5 mm. In the region of the sealing lip 59, the material thickness of the front sealing ring 54 is reduced in a preferred embodiment to about 1 mm.
  • the front sealing ring 54 is biased by the front support ring 58 in the direction of the pump chamber 16 by the sealing lip 69 is pressed out of the center plane 66 obliquely to the longitudinal axis 64 in the direction of the pump chamber 16.
  • the sealing lip 69 rests with its free end portion after insertion of the piston 12 close to its outer periphery.
  • the obliquely aligned to the longitudinal axis 64 sealing lip 69 is acted upon by the pressure prevailing in the pump chamber 16 and thereby pressed against the outside of the piston 12.
  • the radially outer region of the annular bead 68 is pressed by the collar 62 of the front support ring 58 against the wall of the piston chamber 14, so that the piston chamber 14 is reliably sealed relative to the pump chamber 16.
  • a second support element in the form of a rear support ring 72 is arranged in the piston chamber 14, which supports a rear sealing ring 74 in the axial direction.
  • the rear sealing ring 74 is pressed between the end face of the rear support ring 62 and a stepped constriction 76 of the piston chamber 14 and has two V-shaped aligned, each obliquely to the longitudinal axis 64 aligned sealing lips 78, 79.
  • the rear sealing ring 74 forms an oil seal which prevents the rearward penetration of oil into the piston chamber 14.
  • the front support ring 58 defines radially inwardly a first guide surface 81 and at a distance from this, the rear support ring 72 radially inwardly defines a second guide surface 82. At the two guide surfaces 81 and 82 of the piston 12 slidably.
  • the front support ring 58 therefore forms in combination with the rear support ring 72 a piston guide for the piston 12, which is arranged within the piston chamber 14.
  • a further piston guide in the form of a separate, arranged outside the piston pump 10 component can be omitted.
  • the two support rings 58 and 72 are each glued into the piston chamber 14.
  • the front sealing ring 54 can first be inserted into the piston chamber 14 at the rear and then the front support ring 58 can be inserted into the piston chamber 14 and adhesively bonded thereto, biasing the front sealing ring 54 in the direction of the pumping space 16.
  • the rear sealing ring 54 can be inserted into the piston chamber 14, whereby it comes to rest on the stepped constriction 76, and in a subsequent assembly step, the rear support ring 72 can be inserted into the piston chamber 14 and glued to it , Thereafter, the piston 12 can be passed through the two support rings 58 and 72, whereby it slidably bears against the guide surfaces 81 and 82.
  • the two support rings 58 and 72 are arranged at a distance from each other.
  • a front support ring 88 and a rear support ring 92 are used, which together form a preassembled unit 94 and receive a rear sealing ring 96 between them.
  • the rear sealing ring 96 has a retaining ring 97, which is arranged between the front support ring 88 and the rear support ring 92, on which two sealing lips 98, 99 oriented obliquely to the longitudinal axis 64 of the piston 12 are fixed.
  • the front support ring 88 is formed identically in its front region as the above-described in particular with reference to Figure 2 front support ring 58, d. H. it also has an axially projecting collar 62, by means of which the annular bead 68 of the front sealing ring 54 can be pressed radially outward and the sealing lip 69 can be biased in the direction of the pumping space 16.
  • the front support ring 88 has a first guide surface 81 corresponding to the front support ring 58, and the rear support ring 92 includes a second guide surface 82 such that the preassembled unit 94 generally forms a piston guide positionable in the piston chamber 14, as described above was explained in more detail on the two support rings 58 and 72.
  • the preassembled unit 94 has the first guide surface 81 immediately adjacent to a through hole 101 which is aligned after insertion of the preassembled unit 94 in the piston chamber 14 with a laterally opening into this leakage bore 102, on the liquid in the event of leakage liquid from the piston chamber 14th can be dissipated.
  • the piston pump 10 is characterized by a particularly simple assembly of the front sealing ring 54 and by a disposed within the piston chamber 15 piston guide.
  • the manufacturing and assembly costs of the piston pump 10 can be reduced thereby and the service life of the piston pump 10 can be extended due to the integrated piston in the chamber 14 piston guide.

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

Abstract

L'invention concerne une pompe à piston pour un appareil de nettoyage haute pression comprenant au moins une chambre de pompage, dans laquelle plonge un piston pouvant être animé d'un mouvement de va-et-vient, laquelle chambre est reliée à une conduite d'aspiration de liquide, par le biais d'un clapet d'aspiration, et à une conduite de refoulement de liquide sous pression, par le biais d'un clapet de refoulement, chaque piston étant maintenu axialement mobile dans une chambre de piston et entouré d'au moins un anneau d'étanchéité. L'objectif de l'invention est de développer ladite pompe à piston de manière à ce qu'elle puisse être montée de façon économique. A cet effet, au moins un anneau d'étanchéité est pourvu d'un bourrelet annulaire, auquel une lèvre d'étanchéité est adjacente côté intérieur, cet anneau d'étanchéité étant précontrait en direction de la chambre de pompage par un premier élément d'appui dans la chambre de piston.
PCT/EP2008/002815 2007-04-20 2008-04-10 Pompe à piston pour un appareil de nettoyage haute pression WO2008128651A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08735126A EP2140139A1 (fr) 2007-04-20 2008-04-10 Pompe à piston pour un appareil de nettoyage haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007020299.9 2007-04-20
DE102007020299A DE102007020299A1 (de) 2007-04-20 2007-04-20 Kolbenpumpe für ein Hochdruckreinigungsgerät

Publications (1)

Publication Number Publication Date
WO2008128651A1 true WO2008128651A1 (fr) 2008-10-30

Family

ID=39575606

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/002815 WO2008128651A1 (fr) 2007-04-20 2008-04-10 Pompe à piston pour un appareil de nettoyage haute pression

Country Status (3)

Country Link
EP (1) EP2140139A1 (fr)
DE (1) DE102007020299A1 (fr)
WO (1) WO2008128651A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140328698A1 (en) * 2012-01-20 2014-11-06 Alfred Kärcher Gmbh & Co. Kg Piston pump for a high-pressure cleaning appliance

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011054442A1 (de) * 2011-10-12 2013-04-18 Alfred Kärcher Gmbh & Co. Kg Kolbenpumpe für ein Hochdruckreinigungsgerät
BR112014017398A8 (pt) 2012-01-20 2017-07-04 Kaercher Gmbh & Co Kg Alfred bomba de pistão para um aparelho de limpeza a alta pressão
EP2805050B1 (fr) * 2012-01-20 2016-07-27 Alfred Kärcher GmbH & Co. KG Pompe à piston pour un appareil de nettoyage sous haute pression
DE102014213844A1 (de) * 2014-07-16 2016-01-21 Continental Teves Ag & Co. Ohg Kolbenpumpe
CN114431776A (zh) * 2021-04-29 2022-05-06 沙磊 一种病理科用清洁装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB788388A (en) * 1956-08-22 1958-01-02 Angus George Co Ltd Improvements in rubber sealing rings
US3554567A (en) * 1966-03-16 1971-01-12 Carrier Corp Fluid seal
US3811798A (en) * 1972-07-19 1974-05-21 Hydraulic Syst Inc Piston pump with self-lubricating pistons
US3990711A (en) * 1975-05-09 1976-11-09 Hill Ralph W Restrained elastomeric seal ring means
EP0072366A1 (fr) * 1981-08-05 1983-02-16 Vereinigte Edelstahlwerke Aktiengesellschaft (Vew) Joint pour l'étanchéification de dispositifs à haute pression
DE19801146C1 (de) * 1998-01-14 1999-06-24 Kaercher Gmbh & Co Alfred Kolbenpumpe für ein Hochdruckreinigungsgerät

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7611947U1 (fr) * Knorr-Bremse Gmbh, 8000 Muenchen
DE1766338U (de) * 1956-11-16 1958-05-08 Ferch & Nabben Lippendichtung.
DE4027794C2 (de) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulische Radialkolbenpumpe
DE19714844A1 (de) * 1997-04-10 1998-10-15 Mannesmann Sachs Ag Nutring zur Abdichtung von Zylinderflächen
DE19904926A1 (de) * 1999-02-06 2000-08-10 Bosch Gmbh Robert Pumpenaggregat für eine schlupfgeregelte, hydraulische Fahrzeugbremsanlage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB788388A (en) * 1956-08-22 1958-01-02 Angus George Co Ltd Improvements in rubber sealing rings
US3554567A (en) * 1966-03-16 1971-01-12 Carrier Corp Fluid seal
US3811798A (en) * 1972-07-19 1974-05-21 Hydraulic Syst Inc Piston pump with self-lubricating pistons
US3990711A (en) * 1975-05-09 1976-11-09 Hill Ralph W Restrained elastomeric seal ring means
EP0072366A1 (fr) * 1981-08-05 1983-02-16 Vereinigte Edelstahlwerke Aktiengesellschaft (Vew) Joint pour l'étanchéification de dispositifs à haute pression
DE19801146C1 (de) * 1998-01-14 1999-06-24 Kaercher Gmbh & Co Alfred Kolbenpumpe für ein Hochdruckreinigungsgerät

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140328698A1 (en) * 2012-01-20 2014-11-06 Alfred Kärcher Gmbh & Co. Kg Piston pump for a high-pressure cleaning appliance

Also Published As

Publication number Publication date
DE102007020299A1 (de) 2008-10-23
EP2140139A1 (fr) 2010-01-06

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