EP0476450A1 - 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
EP0476450A1
EP0476450A1 EP91115052A EP91115052A EP0476450A1 EP 0476450 A1 EP0476450 A1 EP 0476450A1 EP 91115052 A EP91115052 A EP 91115052A EP 91115052 A EP91115052 A EP 91115052A EP 0476450 A1 EP0476450 A1 EP 0476450A1
Authority
EP
European Patent Office
Prior art keywords
pressure
suction
pump
piston
outer housing
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.)
Granted
Application number
EP91115052A
Other languages
German (de)
English (en)
Other versions
EP0476450B1 (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
Elektra Beckum Lubitz and Co
Original Assignee
Elektra Beckum AG
Elektra Beckum Lubitz and Co
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, Elektra Beckum Lubitz and Co 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.
  • an outer housing which is designed as a cast metal part is initially provided.
  • This outer housing is closed on one side, that is to say it is designed like a pot with an essentially cylindrical recess.
  • Flow channels are molded into the cast material of the housing on the closed side. Screw connections for suction and pressure lines are also formed there.
  • On the open side of the housing there is a fixed cover, also designed as a cast metal part, on which an electric motor with reduction gear and a handle are arranged.
  • a fixed swash plate is arranged on the motor connection side of the outer housing, that is to say on the cover.
  • This swash plate is axially penetrated in the middle by a drive shaft which carries in the interior of the recess a disk-shaped carrier body which is designed as a cast part and is of great thickness.
  • Pump pistons which are arranged parallel to the longitudinal axis of the outer housing and each have a drive end on the swash plate are guided in the piston guides.
  • the pump pistons are spring-loaded in the direction of the swash plate by a compression spring; to accommodate the compression spring, the support body has a correspondingly enlarged recess following each piston guide.
  • the carrier body By rotating the drive shaft, the carrier body, taking the pump pistons guided in the piston guides, can be rotated relative to the swash plate at a correspondingly high rotational speed, so that the drive ends of the pump pistons slide along the swash plate and convert the rotary movement into an axially directed displacement movement of the pump pistons.
  • the pump pistons are therefore carried along by the carrier body.
  • the pump ends of the pump pistons dip into cylindrical recesses in a receiving disk located on the pump connection side of the carrier body and form corresponding working volumes with these cylindrical recesses in the receiving disk.
  • a control disk which has crescent-shaped valve openings and thus serves as a valve arrangement.
  • the control disk and the receiving disk form a surface seal with one another. Valves provided with moving valve elements are not provided and required here, since the valve action is achieved by the interaction of the crescent-shaped valve openings in the control disk with the rotating inlet and outlet openings of the cylindrical recesses.
  • the invention is based on the object of designing the axial piston pump explained at the outset in such a way that it is inexpensive, in particular even in the case of smaller production quantities is adjustable, and in particular that the tool costs in production are as low as possible.
  • Claim 1 shows a solution in which the units are completely self-manageable, that is to say closed overall, while claim 3 shows a semi-integrated solution in which, instead of the valve sleeves of the solution of claim 1, a continuous receiving disk takes over the function of the valve sleeves to a certain extent by: the piston guides are connected there in a tear-proof manner, in particular are screwed in.
  • the units in the axial piston pump according to claim 1 must be combined hydraulically in some way in the outer housing 1, which of course can also serve accordingly a receiving disc, but in the case of a closed outer housing, the bottom of the outer housing can also be designed accordingly.
  • the latter can be achieved in particular if the outer housing is made entirely of plastic, for example with metal reinforcement inserts in the high-pressure areas.
  • the outer housing is no longer designed as a metal (or plastic) casting, which can only be produced with a complicated tool. Rather, the outer housing is formed by a tubular section in the form of a cylinder jacket, which is simply closed by a disk on the open end face. This can also perform additional functions.
  • Such pipe sections are commercially available as sections of seam pipes or seamless pipes as semi-finished products in practically any dimension and material quality. The same applies to panes.
  • the outer housing is thus considerably simplified in terms of production technology.
  • the construction according to the invention can be realized with piston guides rotating about the common longitudinal axis; one would then have to connect the piston guides by means of corresponding connecting elements to form an overall rotating element.
  • These connecting elements could also be commercially available semi-finished products. Then it could remain with the control disk known from the prior art with the crescent-shaped valve openings as a valve arrangement.
  • the teaching according to the invention is preferably used if units of piston guide and pump piston arranged in a fixed manner are provided in the outer housing and the swash plate can be driven in rotation. Then you can choose a suitable valve arrangement with pressure and suction valves.
  • the pressure and suction valves are available as standard semi-finished products. They can also be designed in the range of lower pressures and in particular lower operational loads, that is to say in the field of hobby devices, as lamellar valves or reed valves, as are known from the field of compressors, in particular axial piston compressors.
  • 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
  • FIG. 2 shows, a swash plate 5 which can be driven in rotation here and according to the preferred teaching about the longitudinal axis 4 of the outer housing 1 is arranged on the motor connection side 2. 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.
  • the teaching of the invention can also be applied to a fixed swash plate, as will be explained further below.
  • Fig. 1 it can be seen that in the illustrated embodiment, three pump pistons 10 are provided which are arranged in piston guides 8 parallel to the longitudinal axis 4 of the outer housing 1 and each abut on the swash plate 5 with a drive end 9.
  • 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 in the piston guide 8 to the pump piston 10, 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 connects to inlet / outlet openings 19 of the cylinders 17.
  • each piston guide 8 is an independent, cylinder jacket-shaped part forming a receiving space 20 and in each case a pump piston 10 together with the associated piston guide 8 forms an overall interchangeable unit 21 that the cylinders 17 with their inputs and outlet openings 19 are each integrated in the units 21, 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 which corresponding pressure or suction channels 27, 28 depart, that the valves or the one pressure / suction valves 26 are integrated in the units 21 and that a valve sleeve 22 is in each case connected to the corresponding piston guide 8 in a tear-resistant manner, in particular is screwed and closes the receiving space 20.
  • FIG. 3 shows very clearly what effect the implementation of the teaching ultimately has. While a very large cross-section is effective in the receiving space 20 in printing operation and thus high Tearing forces occur, which are then absorbed via the valve sleeve 22 screwed to the piston guide 8, only a relatively small tearing force acts on the outside in the receiving disk 23, namely with the cross section of the mouth of the pressure channel 34 in the pressure chamber 27 '.
  • the units 21 are inserted at the ends facing the pressure or suction channels 27, 28 into a receiving disc 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 bottom of an outer housing 1 designed in the form of a pot. Then the receiving disk 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, such that one pressure and one suction valve or one double-acting pressure / suction valve 26 per cylinder 17 is provided, from which or from which corresponding pressure or suction channels 27, 28 depart.
  • Fig. 1 shows a further preferred embodiment in so far as it applies here that the outer housing 1 is formed by a cylindrical jacket-shaped pipe section and is closed on the pump connection side 3 by a disk-shaped insert and that, preferably, the receiving disk 23 simultaneously forms the insert.
  • the outer housing 1 is formed by a cylindrical jacket-shaped pipe section and is closed on the pump connection side 3 by a disk-shaped insert and that, preferably, the receiving disk 23 simultaneously forms the insert.
  • the outer housing 1, which was previously designed as a cast part, can now be produced from a commercially available pipe section, which can be closed on the pump connection side 3 by a separate part of appropriate shape.
  • the connection 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. However, it can also be provided that the units 21 are held in the outer housing 1 by a positioning disk 24 provided with corresponding openings for receiving the piston guides 8 and arranged transversely in the outer housing 1. 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.
  • the piston guide 8 each one 4 is a particularly preferred exemplary embodiment, which is characterized in that the cylinder jacket-shaped parts forming the piston guides 8 are formed by correspondingly deformed, in particular step-widened and / or with circumferential, ring-shaped parts Pipe sections provided contact surfaces 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 much lower than the tool costs for a corresponding cast part. The next step is to further reduce 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. 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 there is also a cylinder ring 30 in front of it.
  • the cylinder ring 30 is towards the outside lying spacer ring reduced, in principle it could also be omitted entirely if one then accepts a smaller effect of the displacement of the pump piston 10.
  • a spacer ring 31 also prevents the piston seal 14 from squeezing together.
  • the positioning disk 24 is located between a contact flange on the piston guide 8 and the inner end of the compression spring 12, that is to say the compression spring 12 is supported on the positioning disk 24, the compression spring 12 is supported in the illustration in FIG. 4 Embodiment directly on a contact flange on the piston guide 8, while the positioning disc 24 is supported on an offset, recessed contact flange, which is indicated by dash-dotted lines.
  • the latter construction has advantages in terms of installation technology.
  • one pressure and one suction valve or one double-acting pressure / suction valve 26 is provided for each cylinder 17. This is explained in more detail for the various exemplary embodiments. In all exemplary embodiments, 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 in the exemplary embodiments shown there show that the mounting disk 23 there consists of two or more individual disks.
  • 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 the first alternative of the teaching with 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 leave it completely out, if at the same time the piston guide 8 was correspondingly forward extended.
  • the second alternative of teaching as shown for example in FIG. 2. There is of course a considerable range of possible variations here, but all of them are covered by the two alternatives of claims 1 and 3.
  • FIGS. 3 and 6 it is the case that an annular flange of the pressure / suction valve 26 is clamped between the piston guide 8 and the valve sleeve 22 and from this annular flange the pressure channel 34 into the lower individual disk of the valve disk 22 and protrudes into the pressure channel 27 'or pressure chamber 27' formed there.
  • the valve sleeve 22 forms an annular suction channel 35 which opens into the upper individual disk of the valve disk 22 in the suction channel 28 or suction chamber 28 ′ there.
  • the suction space 28 ′ is embodied here over a large area.
  • the suction space 28 ′ is also divided over a large area by a filter element 28 ′′, namely here a filter fabric supported by support points in the suction space 28 ′.
  • a filter element 28 ′′ namely here a filter fabric supported by support points in the suction space 28 ′.
  • FIGS. 6 and 7 are now particularly simple and expedient with regard to the pressure / suction valve 26.
  • the pressure / suction valve 26 has two leaf valves 26 ', 26 "which are arranged axially one behind the other in the receiving space 20 on different sides of a valve carrier 32 and a pressure channel 34 is arranged angularly offset from a suction channel 35.
  • the contour of an exemplary embodiment of such a valve is shown laterally in FIG Leaf valve 26 ', 26 ". It is easy to see how simple this structure is, such a part can simply be punched out of spring plate.
  • the various parts installed in the outer housing 1 on the pump connection side 3 and / or on the motor connection side 2 are fixed in the axial direction by a circlip 37 in a circumferential groove of the pipe section 1.
  • the fixation by a circlip 37 is only possible according to the invention because the axially occurring tearing forces are overall relatively low for the reasons explained at the beginning.
  • 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 can also be suitably used in printing operation or from the start of printing operation - / Suction valve 26 opens less or more.
  • a bypass circuit it is then possible, by controlling the pressure / suction valve 26 or the pressure / suction valves 26 of all the pump pistons alone, to implement a circulation cycle, as is required for unloaders.
  • 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 punch 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.
  • constructions according to the invention in particular the construction from FIG. 7, even offer 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 entirely in plastic, that is to say also to produce the piston guides 8 from plastic. Then, if this may lead to locally excessive pressures in the receiving disk 23 should, one could also implement metal inserts, for example channels made of metal, at corresponding points.
  • 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 a particularly preferred embodiment, the special features of which can be realized not only in this embodiment, but also in all other constructions. It is essential here 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. In particular, it applies here that 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 that have been passed through and which have been described further above as an alternative. Due to the fact that the sucked-in water is led through the oil space in a kind of cooling cartridge, 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 for 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.
  • the receiving disk 23 with the receptacles 23 'for the units 21 and the pressure or suction channels 27, 28 or the pressure or suction spaces 27', 28 'applies as a single large molded part is executed. It is also particularly preferred that this molded part forms the bottom and end part for the outer housing 1 as a whole.
  • the receiving disk 23 is provided with flange projections 46 projecting outwards with bores 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 exemplary embodiment shown it is made of metal (die-cast aluminum or molded brass part).
  • the receptacles 23' are grouped axially symmetrically around the central axis of the receiving disk 23, that on the insert side of the units 21 In the center of the opposite side, an outlet opening 19 with an axially opening pressure chamber 27 '(collecting chamber) is formed in such a way that this pressure chamber 27' is connected to the receptacles 23 'via three radially extending, sickle-shaped pressure channels 27 and that at the bottom of the receptacle 23' below the laterally opening pressure channels 27 open axial and here also sickle-shaped suction channels 28, which in turn emerge in the form of inlet openings 19 on the end face already mentioned.
  • FIGS. 8 to 11. 11 shows how ingeniously simple the design of the various shaped areas is. In particular, it is important that, due to the circular shape or arc shape of the different areas and channels, the forces occurring are optimally diverted into the material.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
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
DE4039926 1990-12-14
DE19904039926 DE4039926C2 (de) 1990-09-19 1990-12-14 Axialkolbenpumpe, insbesondere für Wasser-Hochdruckreiniger

Publications (2)

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

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016045841A1 (fr) * 2014-09-25 2016-03-31 Mahle International Gmbh Dispositif de pompage, en particulier pompe à piston axial, pour dispositif de récupération de chaleur perdue d'un véhicule automobile
CN112517525A (zh) * 2020-10-14 2021-03-19 张家港三能机电设备有限公司 一种小机械零件用超声波清洗机
CN112555120A (zh) * 2020-12-05 2021-03-26 何自姐 一种尘液两用泵

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB474869A (en) * 1936-02-18 1937-11-09 Teves Kg Alfred Improvements in oil pumps
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
DE2635166A1 (de) * 1975-09-25 1977-03-31 Lear Siegler Inc Koaxiales einlass- und auslassventil
EP0177925A1 (fr) * 1984-10-08 1986-04-16 K.E.W. Industri A/S Ensemble moteur-pompe pour une unité de nettoyage à haute pression
EP0312862A2 (fr) * 1987-10-17 1989-04-26 Vdb-Patent Ag Dispositif de nettoyage à haute pression

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB474869A (en) * 1936-02-18 1937-11-09 Teves Kg Alfred Improvements in oil pumps
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
DE2635166A1 (de) * 1975-09-25 1977-03-31 Lear Siegler Inc Koaxiales einlass- und auslassventil
EP0177925A1 (fr) * 1984-10-08 1986-04-16 K.E.W. Industri A/S Ensemble moteur-pompe pour une unité de nettoyage à haute pression
EP0312862A2 (fr) * 1987-10-17 1989-04-26 Vdb-Patent Ag Dispositif de nettoyage à haute pression

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016045841A1 (fr) * 2014-09-25 2016-03-31 Mahle International Gmbh Dispositif de pompage, en particulier pompe à piston axial, pour dispositif de récupération de chaleur perdue d'un véhicule automobile
US10280905B2 (en) 2014-09-25 2019-05-07 Mahle International Gmbh Pumping device for a waste heat recovery apparatus in a motor vehicle
CN112517525A (zh) * 2020-10-14 2021-03-19 张家港三能机电设备有限公司 一种小机械零件用超声波清洗机
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
CN112555120A (zh) * 2020-12-05 2021-03-26 何自姐 一种尘液两用泵
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

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DK0476450T3 (da) 1995-04-10
DE59104762D1 (de) 1995-04-06
EP0476450B1 (fr) 1995-03-01

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