EP0476450B1 - Pompe à pistons axiaux, particulièrement pour nettoyeur haute pression à eau - Google Patents

Pompe à pistons axiaux, particulièrement pour nettoyeur haute pression à eau Download PDF

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Publication number
EP0476450B1
EP0476450B1 EP19910115052 EP91115052A EP0476450B1 EP 0476450 B1 EP0476450 B1 EP 0476450B1 EP 19910115052 EP19910115052 EP 19910115052 EP 91115052 A EP91115052 A EP 91115052A EP 0476450 B1 EP0476450 B1 EP 0476450B1
Authority
EP
European Patent Office
Prior art keywords
intake
delivery
channels
axial piston
recesses
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.)
Expired - Lifetime
Application number
EP19910115052
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German (de)
English (en)
Other versions
EP0476450A1 (fr
Inventor
Lothar Hartmann
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.)
Elektra Beckum AG
Original Assignee
Elektra Beckum AG
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
Priority claimed from DE19904039926 external-priority patent/DE4039926C2/de
Application filed by Elektra Beckum AG filed Critical Elektra Beckum AG
Publication of EP0476450A1 publication Critical patent/EP0476450A1/fr
Application granted granted Critical
Publication of EP0476450B1 publication Critical patent/EP0476450B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/1037—Flap valves
    • F04B53/104—Flap valves the closure member being a rigid element oscillating around a fixed point
    • 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
    • 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
    • F04B53/08—Cooling; Heating; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to an axial piston pump, in particular for water high-pressure cleaners, with the features of the preamble of claim 1.
  • a drive shaft which carries a swash plate guided on roller bearings, is mounted in a sealed manner in the center on the bottom of a pot-like outer housing that is open on one side.
  • the pot-like outer housing is closed on the open side by a one-piece pump head designed as a casting, which also forms a bearing for the drive shaft in the middle.
  • the pump head is firmly screwed to the pot-like outer housing; in the pump head there are a total of ten receptacles running parallel to each other in the direction of the central axis, all of which are open to both end faces.
  • the recordings are arranged in a circle.
  • an overall interchangeable unit (cartridge) which has an outer sleeve which essentially fills the full length of the receptacle, a pump piston which is displaceably guided in the outer sleeve and a pressure valve installed at the end of the outer sleeve.
  • the outer sleeve forms on the one hand a piston guide for the pump piston, on the other hand a cylinder which limits a working volume with the pump end of the pump piston.
  • the drive ends of the pump pistons rest on the swash plate, so that the pump pistons are moved back and forth in the outer sleeves in the axial direction by rotating the swash plate.
  • the suction valve which belongs to every cartridge, is integrated in the pump piston.
  • In each pump piston there is an axially extending suction channel which opens at the pump end and in which the suction valve is arranged.
  • the water sucked in by the pump pistons is thus sucked in here through the drive chamber of the swash plate, specifically through a suction opening with an internal thread arranged on the jacket of the outer housing, to which a suction line can be connected.
  • Such a suction line is usually provided with a filter insert at the suction opening.
  • axial piston pump has a high delivery rate, as is required in particular for water high-pressure cleaners, such a suction filter quickly clogs up.
  • Optimal integration of an intake filter in an axial piston pump would not only be advantageous in terms of intake technology, but would also have a positive effect on the production costs of the axial piston pump.
  • the end of the outer housing is formed by a receiving disk having corresponding recesses.
  • This receiving disk has, as units, exchangeable piston guides in the recesses, a pressure valve and a suction valve being provided for each cylinder, from which corresponding pressure channels or suction channels depart.
  • the valves are integrated in the piston guide.
  • the recesses for receiving the piston guides are arranged axially symmetrically around the central axis to the receiving disc.
  • the recesses are continuous in the receiving disc, that is, open from both sides.
  • a suction opening with an axially opening suction chamber is formed in the center, which is connected to the respective recesses via radially extending suction channels.
  • the recesses are closed at the end by a sealing plug and the pressure channels extend into an annular collecting space which is connected to a common external pressure connection. None is sucked out here by filtering the sucking liquid, in particular the sucking water.
  • the invention has for its object to optimize the axial piston pump explained in the introduction, in such a way that it can be produced inexpensively even with less large production quantities.
  • a recess corresponding to the flat shape of the receiving disk is made as a suction space in the receiving disk which carries or forms the cylinder anyway. This creates a common suction space for all cylinders.
  • this is now used particularly, namely by a large-area filter element that divides the suction space.
  • the large area of the suction chamber is therefore used for large-area filtering.
  • Such large-area filtering has the advantage that Large-area filter element with high delivery capacities of the axial piston pump clogged much less quickly than known filter elements located at small-area suction openings.
  • the filtering is integrated in the axial piston pump itself. The advantages in terms of intake technology are thus achieved with little outlay in terms of production technology. In particular, the axial piston pump can be produced inexpensively even in the case of less large production quantities.
  • the axial piston pump initially has an outer housing 1 with a motor connection side 2 and a pump connection side 3. In Fig. 1 you can see from the motor connection side 2 in the outer housing 1st
  • a swash plate 5 which can be driven in rotation about the longitudinal axis 4 of the outer housing 1 is arranged on the motor connection side 2.
  • the housing 6 of the electric motor serving for the rotary drive and a drive shaft 7 for the swash plate 5 are indicated on the right.
  • Fig. 1 it can be seen that three pump pistons 10 are provided parallel to the longitudinal axis 4 of the outer housing 1 in piston guides 8, each with a drive end 9 abutting the swash plate 5.
  • Each piston guide 8 and each pump piston 10 includes an abutment disk 11 attached to the pump piston 10, a compression spring 12 inserted between the abutment disk 11 and the piston guide 8, possibly also a support disk 13 attached to the pump piston 10 in the piston guide 8, and at least one piston seal 14.
  • the piston guide 8 has a sliding insert 15 for the pump piston 10, which ensures that the sliding friction of the pump piston 10 in the piston guide 8 is very low.
  • PTFE polytetrafluoroethylene
  • the pump ends 16 of the pump pistons 10 opposite the drive ends 9 are axially displaceably received in cylinders 17, each of which includes a working volume 18 with the pump ends 16.
  • This working volume 18 is large at the top in FIG. 2 and particularly small at the bottom in FIG. 2.
  • a valve arrangement is connected to the inlet / outlet openings 19 of the cylinders 17.
  • each piston guide 8 is an independent, cylinder-jacket-shaped part that forms a receiving space 20 and a pump piston 10 together with the associated piston guide 8 forms an overall interchangeable unit 21 that the cylinders 17 with their inlet and outlet openings 19 each in the units 21 are integrated in that a pressure and a suction valve or a double-acting pressure / suction valve 26 is provided for each cylinder 17, from which or from the corresponding pressure or suction channels 27, 28 depart that the valves or a pressure / suction valve 26 are integrated in the units 21 and that for this purpose a valve sleeve 22 is connected to the corresponding piston guide 8 in a tear-resistant manner, in particular is screwed, and closes the receiving space 20.
  • the units 21 are inserted at the ends facing the pressure or suction channels 27, 28 into a receiving disk 23 which is arranged transversely in the outer housing 1 and has corresponding recesses.
  • the recesses in the receiving disk 23 for the use of the units 21 with the front edges can also be formed in a base of an outer housing 1 designed in the form of a pot. Then the receiving plate 23 would be formed from the bottom of the outer housing 1. However, it could also be arranged on the floor in such a pot-like outer housing 1.
  • each piston guide 8 is an independent, cylinder-jacket-shaped part which forms a receiving space 20 and in each case a pump piston 10 together with the associated piston guide 8 forms an overall replaceable unit 21 such that the cylinders 17 with their inlet and outlet openings 19 each integrated into the units 21 or formed by a receiving disc 23 arranged transversely in the outer housing 1 and having corresponding recesses, that one pressure and one suction valve or one double-acting pressure / suction valve 26 are provided for each cylinder 17 from which or from which corresponding pressure or suction channels 27, 28 depart.
  • the piston guides 8 are tear-proof connected to the receiving disk 23, in particular screwed, and the receiving spaces 20 of all piston guides 8 are closed by the receiving disk 23 and that the valves or the one pressure / suction valve 26 are integrated in the units 21, namely in the receiving spaces 20 are arranged.
  • This concept is implemented in the exemplary embodiments of FIGS. 2, 4 and 7.
  • the high tear-open forces are also kept away from the outer housing 1, namely predominantly absorbed by the partial cartridges, in particular screwed, connected to the receiving disk 23 in a tear-resistant manner.
  • Fig. 2 it can be seen that the same applies here as in the first alternative.
  • Fig. 1 shows that the outer housing 1 is formed by a cylindrical tubular section and is closed on the pump connection side 3 by a disk-shaped insert and that, preferably, the receiving plate 23 forms the insert at the same time.
  • the outer housing 1 can be made from a commercially available pipe section, which can be closed on the pump connection side 3 by a separate part of appropriate shape.
  • the connecting flange provided on the pipe section on the motor connection side 2 can also be formed on the pipe material using modern techniques.
  • the units 21 can be let into the receiving disk 23 to a greater or lesser extent. This applies to the pump end of the units 21. If it is let into a receiving disk 23 sufficiently far, a further lateral guide at the other end, that is to say in the region of the piston guides 8 as such, is not required. That shows e.g. B. Fig. 4. But it can also be provided that the units 21 are held in the outer housing 1 by means of corresponding openings for receiving the piston guides 8, arranged transversely in the outer housing 1, positioning disk 24. This version is shown in FIGS. 2 and 6. It is also indicated in FIG. 1. It applies that the positioning disc 24 is provided with circumferential seals 25 on the circumference and at the openings.
  • the positioning disc 24 has a component which is also available as a commercially available semi-finished product processed with simple processing steps.
  • This positioning disk 24 can fulfill an additional function, namely by dividing the pipe section 1 into a “water part” on the left in FIG. 2, on the top in FIG. 6 and an “oil part” on the right in FIG. 2, below in FIG. 6 and seals both parts against each other. This ensures that you work oil-free in the water part and can be spared water ingress in the oil part.
  • Fig. 2 indicates the piston guide 8 of each unit 21 as a technically complicated component, possibly still as a cast part
  • Fig. 4 shows that the cylinder-jacket-shaped parts forming the piston guides 8 by correspondingly deformed, in particular step-widened and / or with circumferential annular contact surfaces provided pipe sections are formed.
  • Modern forming technology makes it possible to subsequently realize relatively large jumps in diameter in pipe sections available as semi-finished products, the associated tool costs being incomparably lower than the tool costs for a corresponding cast part. In this way, one obtains a reduction in the manufacturing costs caused by tool costs.
  • FIGS. 2, 3 and 4 show constructions in which the cylinders 17 with their inlet and outlet openings 19 are each integrated in the units 21.
  • FIGS. 3 and 4 there is in front of the support ring 29, which is present in all cases, the piston seal 14, which is present in all cases, but in front of it there is also a cylinder ring 30.
  • the cylinder ring 30 is further out lying spacer ring reduced, in principle it could also be omitted entirely if one accepts a lower effect of the displacement of the pump piston 10.
  • a spacer ring 31 also prevents the piston seal 14 from squeezing together.
  • a pressure valve and a suction valve or a double-acting pressure / suction valve 26 are provided for each cylinder 17. This is explained in more detail for the various examples. In all examples, however, a double-acting pressure / suction valve 26 is provided here. 5 shows a separate structural unit in this form, the pressure / suction valve 26 shown there is known from the prior art and is commercially available (US Pat. No. 4,032,263).
  • FIGS. 3 and 6 show that the receiving disk 23 consists of two or more individual disks there.
  • common pressure channels 27 or suction channels 28 are worked into the receiving disk 23 or in the individual disks of the receiving disk 23 or between the individual disks for all units 21, in particular introduced through a bore, or pressure or suction spaces 27 '. , 28 'are formed.
  • the machining operations are very simple in nature.
  • FIG. 3 shows a valve sleeve 22 designed as a coupling element. It would be possible to have the valve sleeve 22 degenerate to a flat end cover or to omit it entirely if the piston guide 8 was simultaneously extended accordingly to the front. The second alternative is then realized, as shown for example in FIG. 2.
  • the suction chamber 28 ' is now divided over a large area by a filter element 28'', namely here a filter fabric supported via support points in the suction chamber 28'.
  • a filter element 28'' namely here a filter fabric supported via support points in the suction chamber 28'.
  • the pressure / suction valve 26 has two leaf valves 26 ′, 26 ′′, which are arranged in the receiving space 20 axially one behind the other on different sides of a valve support 32, and a pressure channel 34 is angularly offset from a suction channel 35. 6, the contour of such a leaf valve 26 ', 26' 'is drawn out to the side. It is easy to see how simple this structure is, such a part can simply be punched out of spring plate. It can also be seen that there is a free space in the angularly offset region of a leaf valve for the passage of a flow channel to another leaf valve.
  • a pressure / suction valve 26 can also be converted into a type of bypass valve with an unloader function, namely that the suction section of the pressure is also suitable in the printing mode or from the start of the printing operation - / Suction valve 26 opens less or more.
  • 5 shows a stamp 39 entering the valve disk 32, which externally mechanically influences a valve plate 40 of the suction part of the pressure / suction valve 26, so that the valve plate 40 does not completely close even in the fully advanced position. How and to what extent the stamp 39 is controlled externally can be left open, this is only indicated by the direction arrow.
  • the swash plate 5 carries a sliding coating 38 or sliding pad made of PTFE or the like.
  • FIG. 7 even offers the possibility in lower pressure ranges, for example in the case of hobby high-pressure cleaning devices in the range up to 100 bar, to work completely in plastic, so also to produce the piston guides 8 made of plastic. If this should lead to locally excessive pressures in the receiving disk 23, metal inserts, for example channels made of metal, could also be implemented at corresponding locations.
  • FIGS. 3 and 6 offer particularly advantageous conditions for a design made of corrosion-resistant materials.
  • the parts that are subjected to high pressure or tear forces could be made of stainless steel, the parts that were subjected to less pressure could be made of plastic.
  • Fig. 7 shows that the suction channels 28 or the common suction channel or suction chamber 28 'is preceded by a suction flow diversion 41 and that the suction flow diversion 41 has a line section 42 projecting into the oil chamber facing the swash plate 5.
  • the line section 42 projecting into the oil chamber facing the swash plate 5 is designed as a coaxial tube.
  • This suction flow diversion 41 has a cooling effect similar to that of the pump pistons with suction lines which have been carried out and which have been described above as an alternative.
  • the fact that the sucked-in water is passed through the oil space in a kind of cooling cartridge means that the oil located there is sufficiently cooled.
  • FIG. 7 shows another way of guiding the pressure and suction channels 34, 35, which here are not arranged coaxially, as is required in the case of the full cartridge systems, but simply lie next to one another in the receiving disk 23 .
  • the high-pressure piston seal 14 is supported on the back by a support ring 29, which in turn is held on the inner circumference of the piston guide 8 by a bore ring 43 inserted in a groove. Between the oil piston seal 14 and the support ring 29 there is a leak oil chamber 44, from which a leak oil channel 45 leads back into the oil chamber, so that lubricating oil which has been drawn through can return to the oil chamber.
  • this molded part forms the base and end part for the outer housing 1 as a whole.
  • the receiving plate 23 is provided with outwardly projecting flange lugs 46 with holes 47 for tensioning and connecting screws. Given the appropriate pressure conditions, this part can even be made of plastic because of the relationships explained at the beginning, but in the example shown it is made of metal (die-cast aluminum or molded brass part).
  • FIGS. 8 to 11. 11 shows in particular how ingeniously simple the design of the various shaped areas is. In particular, it is important that because of the circular shape or arc shape of the different areas and channels, the forces occurring are optimally diverted into the material.

Claims (10)

  1. Pompe à pistons axiaux, en particulier pour nettoyeur à eau haute pression, comportant un boîtier externe (1) avec au moins deux pistons de pompe (10) agencés parallèlement à l'axe longitudinal (4) du boîtier externe (1) dans des glissières de pistons (8), s'appliquant respectivement, à une extrémité d'entraînement (9), sur un plateau oscillant (5), des cylindres (17) recevant les extrémités de pompage opposées (16) des pistons (10) de manière à assurer leur déplacement axial, cylindres qui enserrent respectivement avec les extrémités de pompage (16) un volume de travail (18), et un agencement de soupapes raccordées aux ouvertures d'admission et d'échappement (19) des cylindres (17), chaque cylindre (17) étant équipé d'une soupape de compression et une soupape d'aspiration ou une soupape de compression/aspiration (26) à double effet, d'où partent des canaux de compression ou d'aspiration correspondants (27, 28), les cylindres (17) étant insérés aux extrémités tournés vers les canaux de compression ou d'aspiration (27, 28) dans un plateau récepteur (23) agencé transversalement dans le boîtier externe (1) et présentant des évidements correspondants (23') de préférence circulaires ou bien les cylindres (17) étant formés d'un disque récepteur (23) agencé transversalement dans le boîtier externe (1) et présentant des évidements correspondants (23') de préférence de forme circulaire, de préférence chaque piston de pompe (10) formant conjointement avec la glissière de piston (8) qui lui est affectée une unité (21) globalement interchangeable, caractérisée en ce que, dans le disque récepteur (23) est formé au moins un espace d'aspiration (28'), qui s'étend sur une partie sensible de la section transversale du disque récepteur (23), et en ce que l'espace d'aspiration (28') est divisé, de manière correspondante, sur une grande surface par un élément de filtration (28''), en particulier un tissu de filtration.
  2. Pompe à pistons axiaux selon la revendication 1, caractérisée en ce que l'élément de filtration (28'') placé dans l'espace d'aspiration (28') s'appuie sur des points de support répartis sur une grande surface.
  3. Pompe à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que des canaux de compression (27) ou des canaux d'aspiration (28) communs à tous les cylindres (17) sont enfoncés dans le disque récepteur (23) en y formant également un espace de compression (27') commun.
  4. Pompe à pistons axiaux selon l'une des revendication 1 à 3, caractérisée en ce que le disque récepteur (23) est constitué de deux ou plusieurs disques individuels et l'espace d'aspiration (28'), l'espace de compression (27'), les canaux de compression (27) et les canaux d'aspiration (28) sont enfoncés ou conformés dans les disques individuels du disque récepteur ou entre les disques individuels.
  5. Pompe à pistons axiaux selon l'une quelconque des revendications 1 a 4, caractérisée en ce qu'une conduite de dérivation du flux d'aspiration (41) est agencée en amont des canaux d'aspiration (28) ou du canal d'aspiration ou de l'espace d'aspiration commun (28') et en ce que la conduite de dérivation du flux d'aspiration (41) présente une section de conduite (42) se dressant dans l'espace d'huile tourné vers le plateau oscillant (5).
  6. Pompe à pistons axiaux selon la revendication 5, caractérisée en ce que la section de conduite (42) se dressant dans l'espace d'huile tourné vers le plateau oscillant (5) se présente sous la forme d'un tube coaxial.
  7. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le disque récepteur (23) avec les évidements (23') et les canaux de compression ou d'aspiration (27, 28) ou avec les espaces de compression ou d'aspiration communs (27', 28') se présente sous la forme d'une grosse pièce moulée, au moins deux évidements (23') sont prévus agencés selon une symétrie axiale autour de l'axe central du disque récepteur (23), sur le côté opposé au côté d'aménagement des évidements (23'), au centre, est moulée une ouverture d'échappement (19) avec un espace de compression (27') qui y débouche axialement, l'espace de compression (27') est en communication, via des canaux de compression (27) s'écartant radialement, avec les évidements (23) et, au fond des évidements (23'), en dessous des canaux de compression (27), débouchent des canaux d'aspiration axiaux (28) qui débouchent eux-mêmes dans des ouvertures d'admission (19) sur le côté en regard du côté d'aménagement des évidements (23').
  8. Pompe à pistons axiaux selon la revendication 7, caractérisée en ce que le disque récepteur (23) forme une partie de fond et de fermeture ou une partie rapportée du boîtier externe (1).
  9. Pompe à pistons axiaux selon la revendication 7 ou 8, caractérisée en ce qu'il est prévu trois évidements (23') qui sont agencés en symétrie axiale autour de l'axe central du disque récepteur (23).
  10. Pompe à pistons axiaux selon l'une quelconque des revendications 1 à 9, caractérisée en ce que les canaux de compression (27) et/ou les canaux d'aspiration (28) sont conformés en croissant.
EP19910115052 1990-09-19 1991-09-06 Pompe à pistons axiaux, particulièrement pour nettoyeur haute pression à eau Expired - Lifetime EP0476450B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE4029674 1990-09-19
DE4029674 1990-09-19
DE4030412 1990-09-26
DE4030412 1990-09-26
DE19904039926 DE4039926C2 (de) 1990-09-19 1990-12-14 Axialkolbenpumpe, insbesondere für Wasser-Hochdruckreiniger
DE4039926 1990-12-14

Publications (2)

Publication Number Publication Date
EP0476450A1 EP0476450A1 (fr) 1992-03-25
EP0476450B1 true EP0476450B1 (fr) 1995-03-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19910115052 Expired - Lifetime EP0476450B1 (fr) 1990-09-19 1991-09-06 Pompe à pistons axiaux, particulièrement pour nettoyeur haute pression à eau

Country Status (3)

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EP (1) EP0476450B1 (fr)
DE (1) DE59104762D1 (fr)
DK (1) DK0476450T3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014219488A1 (de) * 2014-09-25 2016-03-31 Mahle International Gmbh Pumpvorrichtung, insbesondere Axialkolbenpumpe, für eine Abwärmenutzungseinrichtung eines Kraftfahrzeugs
CN112517525B (zh) * 2020-10-14 2022-02-01 昆山众劲机械有限公司 一种小机械零件用超声波清洗机
CN112555120B (zh) * 2020-12-05 2021-09-07 福建永越智能科技股份有限公司 一种尘液两用泵

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE680810C (de) * 1936-02-18 1939-09-07 Teves Kg Alfred Kolbenpumpe
FR988402A (fr) * 1943-12-27 1951-08-27 Messier Sa Perfectionnements aux pompes hydrauliques
US2945444A (en) * 1957-09-23 1960-07-19 Dynex Inc Hydraulic pump
US3180277A (en) * 1963-03-07 1965-04-27 Frank Wheatley Pump & Valve Ma Valve system for reciprocating pump
GB1063725A (en) * 1965-03-24 1967-03-30 Oswalds And Ridgway Ltd Improvements in hydraulic pumps
US4032263A (en) * 1975-09-25 1977-06-28 Lear Siegler, Inc. Pump with coaxial inlet and outlet valve arrangement
DK481284A (da) * 1984-10-08 1986-04-09 Knud Erik Westergaard Motorpumpeenhed til et hoejtryksrenseapparat
DE8713954U1 (fr) * 1987-10-17 1987-12-03 Carl Platz Hochdrucktechnik Gmbh, 6710 Frankenthal, De

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DK0476450T3 (da) 1995-04-10
EP0476450A1 (fr) 1992-03-25
DE59104762D1 (de) 1995-04-06

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