EP2396550B1 - Motor pump unit - Google Patents

Motor pump unit Download PDF

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Publication number
EP2396550B1
EP2396550B1 EP09776377.5A EP09776377A EP2396550B1 EP 2396550 B1 EP2396550 B1 EP 2396550B1 EP 09776377 A EP09776377 A EP 09776377A EP 2396550 B1 EP2396550 B1 EP 2396550B1
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EP
European Patent Office
Prior art keywords
motor
annular space
housing
motor housing
pump unit
Prior art date
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EP09776377.5A
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German (de)
French (fr)
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EP2396550A1 (en
Inventor
Walter Schiffhauer
Dieter Plachke
Lanfranco Pol
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alfred Kaercher SE and Co KG
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Alfred Kaercher SE and Co KG
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Application filed by Alfred Kaercher SE and Co KG filed Critical Alfred Kaercher SE and Co KG
Priority to PL09776377T priority Critical patent/PL2396550T3/en
Publication of EP2396550A1 publication Critical patent/EP2396550A1/en
Application granted granted Critical
Publication of EP2396550B1 publication Critical patent/EP2396550B1/en
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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
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors

Definitions

  • the invention relates to a motor pump unit for a high-pressure cleaning device having a liquid-cooled electric motor and a pump, wherein the electric motor has a motor housing which is surrounded by a cylinder jacket-shaped cooling housing to form an annulus provided with an annular space inlet and an annular space, and wherein the pump with the annular space connected suction inlet for sucking liquid and a pressure outlet for dispensing liquid and wherein the pumped by the pump liquid to be fed to the annular space inlet and the cooling housing inside at least one flow guide rib for guiding the liquid in the annular space.
  • Such motor pump units are from the DE 10 2007 009 394 A1 known. They are used in high-pressure cleaning devices in which a liquid, preferably water, can be pressurized and then discharged via the pressure outlet. At the pressure outlet, a high-pressure hose can be connected, which carries at its free end, for example, a spray lance. This provides the ability to direct a high pressure jet of liquid at an object, for example, to clean the object.
  • the drive of the pump by means of an electric motor, which is cooled by the liquid which is supplied to the pump.
  • the motor housing is surrounded by a cylinder jacket-shaped cooling housing, wherein an annular space is formed between the motor housing and the cooling housing, which can be supplied via an annulus inlet of the pump to be pumped liquid.
  • the liquid can flow through the annular space and pass through the annular space outlet to the suction inlet of the pump so that it can then be pressurized.
  • Flow guide in the form of Strömungsleitrippen which are arranged on the inside of the cooling housing, pass the liquid through the annulus.
  • the Strömungsleitrippen are in the motor pump unit, which in the DE 10 2007 009 394 A1 is described, designed as support ribs, with the help of which the cooling housing is supported on the motor housing.
  • the pump will be connected to the public water supply network. This has the consequence that within the annular space prevailing in the water supply network discharge pressure of a few bar, for example, 5 to 10 bar, prevails.
  • discharge pressure of a few bar, for example, 5 to 10 bar.
  • Object of the present invention is to develop a motor pump unit of the type mentioned in such a way that it is ensured that even in the long term no liquid can escape from the annulus.
  • the motor housing is subject to unavoidable vibration. These can lead to a relative movement between the flow guide ribs of the cooling housing and the motor housing. If the flow guide ribs lie directly against the motor housing, the flow guide ribs can damage the surface of the motor housing by rubbing or scratching. As a result, the surface structure of the motor housing can be affected, and this in turn can cause liquid from the annulus through the damaged motor housing can enter into the interior of the electric motor.
  • the invention provides that the Strömungsleitrippen occupy a distance from the motor housing, that is, between the Strömungsleitrippen and the motor housing, a gap extends.
  • a flow guide rib is arranged between the annular space inlet and the annular space outlet. This ensures that over The liquid entering the annular space can not directly reach the annular space outlet, but much of the liquid, starting from the annular space inlet, flows around the entire motor housing, only then to reach the annular space outlet.
  • the cooling housing has a plurality of circumferentially offset from one another arranged Strömungsleitrippen, each comprising a passage, wherein the passages of adjacent Strömungsleitrippen are axially offset from one another.
  • the Strömungsleitrippen define a total of a labyrinth-like, in the circumferential direction around the motor housing leading around the flow path from the annular space inlet to the annulus outlet. This results in a particularly effective cooling of the electric motor result.
  • the height of the gap between the at least one flow guide rib and the motor housing is preferably at least 0.3 mm. In particular, a height of 0.5 mm and more has proved to be advantageous. It can be provided, for example, that the height of the gap between the at least one flow guide rib and the motor housing is at least 1 mm.
  • the height of the Strömungsleitrippen is preferably at least 1 mm. It can be provided, for example, that the flow guide ribs have a height of at least 2 mm. In an advantageous embodiment, a height of at least 3 mm is provided.
  • the height of the flow guide ribs is a multiple of the height of the gap.
  • the motor housing carries a corrosion protection layer.
  • the motor housing may, for example, be coated with a special protective material. But it can also be provided that the corrosion protection layer is designed as an oxidation layer of the motor housing.
  • the motor housing may preferably be made of a deep-drawn steel, which is oxidized on the surface.
  • the cooling housing is preferably made of plastic.
  • Plastic housings are usually prone to vibration. It is therefore particularly advantageous for plastic housings when the at least one flow guide rib is at a distance from the motor housing in order to avoid surface damage.
  • the annular space is sealed in a particularly preferred embodiment by means of a front and a rear sealing ring, which in the radial direction between the motor housing and the cooling housing are trapped.
  • the sealing of the annular space in the region of the sealing rings is thus effected by a radial load of the sealing rings.
  • the motor housing facing the pump has an outwardly projecting annular flange, which is adjoined by an annular sealing surface against which the front sealing ring rests.
  • the outwardly projecting annular flange of the motor housing can be clamped between a bearing plate, which is formed by a drive housing of the pump, and an end face of the cooling housing.
  • On the rear side facing away from the pump of the outwardly projecting annular flange of the front sealing ring may be positioned, which is clamped in the radial direction between an adjoining the annular flange annular sealing surface of the motor housing and a corresponding annular sealing surface of the cooling housing.
  • the motor housing facing away from the pump has a cylinder-jacket-shaped collar which is surrounded by a cylinder jacket-shaped projection of the cooling housing with the interposition of the rear sealing ring.
  • the cylinder jacket-shaped collar of the pot-shaped motor housing can extend between the bottom and the jacket of the motor housing.
  • a cylinder jacket-shaped projection of the cooling housing can be aligned concentrically with the cylinder jacket-shaped collar of the motor housing be, and between the collar and the neck of the rear sealing ring can be braced in the radial direction.
  • a motor pump unit 10 is shown schematically with a liquid-cooled electric motor 11 and a pump 12.
  • the electric motor 11 has in the usual way a rotor 14 which is surrounded by a stator 15.
  • a pot-shaped motor housing 17 connects to the outside, which is made of a deep-drawn steel. It has a cylinder jacket-shaped peripheral wall 18 and a bottom 19.
  • the bottom 19 forms an axially outwardly directed receptacle 20 for a first bearing 21 of a motor shaft 22.
  • a second bearing 23 for the motor shaft 22 is disposed on a bearing plate 26, of a Drive housing 28 of the pump 12 is formed.
  • the motor housing 17 is surrounded in the circumferential direction by a cylinder jacket-shaped cooling housing 30, wherein between the motor housing 17 and the cooling housing 30, an annular space 32 is arranged, which completely surrounds the motor housing 17 in the circumferential direction.
  • an annular space inlet 33 of the cooling housing 30 liquid can be supplied to the annular space 32, which then flows through the annular space 32.
  • an annular space outlet 34 of the cooling housing 30 the liquid can flow out of the annular space 32.
  • the cooling housing 30 carries on the inside a plurality of circumferentially uniformly spaced Strömungsleitrippen 36 which protrude radially into the annular space 32, but they do not touch the motor housing 17, but extends between each Strömungsleitrippe 36 and the motor housing 17, a gap 37 with a height of about 1 mm.
  • the height of the Strömungsleitrippen 36 in the radial direction is at least 2 mm. It is advantageous if the height of the Strömungsleitrippen 36 is at least twice as large as the height of the gap 37. It is particularly advantageous if the height of the Strömungsleitrippen 36 in the radial direction a multiple of the height of the gap 37 carries.
  • the Strömungsleitrippen 36 have a height of at least 3 mm and the height of the gap 37 may be at most 1 mm.
  • the Strömungsleitrippen 36 each have a passage 38 through which liquid, which is supplied to the annular space 32, can flow therethrough.
  • the passages 38 of adjacent Strömungsleitrippen 36 are axially offset from one another, so that the Strömungsleitrippen 36 a labyrinthine, in the circumferential direction around the motor housing 17 around leading flow path from the annulus inlet 33 to the annulus outlet 34 define.
  • the annular space 32 is sealed by a front sealing ring 41 and a rear sealing ring 42.
  • the front sealing ring 41 is arranged on the side facing away from the pump 12 of an outwardly projecting annular flange 44 of the motor housing 17, which is clamped between the bearing plate 26 and the pump 12 facing the end face of the cooling housing 30.
  • the sealing of the annular space 32 in the region of the front sealing ring 41 is effected by radial loading of the sealing ring 41. This is braced between an annular sealing surface 45 of the motor housing 17 and a corresponding annular sealing surface 46 of the cooling housing 30 in the radial direction.
  • the rear sealing ring 42 abuts against a cylinder jacket-shaped collar 48 of the motor housing 17, which extends in the transition region between the bottom 19 and the peripheral wall 18 concentric with the motor shaft 22.
  • the collar 48 is surrounded by a cylinder jacket-shaped projection 49 of the cooling housing 30, which is aligned concentrically with the collar 48.
  • Between the collar 48 and the projection 49 of the rear sealing ring 42 is braced in the radial direction. In the axial direction, it is supported by a radially inwardly directed return of the cooling housing 30.
  • the motor housing 17 is, it has already been noted, made of a deep-drawing steel. This has superficially on an oxidation layer, the acts as a corrosion protection layer and ensures that the motor housing 17 is permanently impermeable to water. Since the Strömungsleitrippen 36 occupy a distance from the motor housing 17, it is ensured that the superficial oxidation layer of the motor housing 17 is not affected by vibrations of the motor housing 17, which could result in damage to the surface of the motor housing 17, if the Strömungsleitrippen 36, the surface of the Motor housing 17 could touch.
  • the pump 12 has a suction inlet 51 and a pressure outlet 52 in the usual way.
  • Parallel to the motor shaft 22 aligned piston 54 of the pump 12 are applied to a swash plate 56 which is adjacent to the drive housing 28, the bearing plate 26, and coupled to the motor shaft 22.
  • the piston 54 are shown in the drawing at a distance from the swash plate 56. In fact, they bear against the swash plate 56 on the face side and are thereby driven to a reciprocating motion. With their end facing away from the swash plate 56, the pistons 54 dive into a pumping space in the usual way, so that liquid can be sucked into the pumping space from the suction inlet 51 and released under pressure via the pressure outlet 52.
  • the conduit arrangement 60 comprises a supply line 61, which is connected to a first cooling channel 62 of the drive housing 28, which in turn is connected in a liquid-tight manner to the annular space inlet 33.
  • the conduit arrangement 60 also has a connection line 63, which is aligned parallel to the supply line 61 and a parallel to the first cooling channel 62 aligned second cooling channel 64 of the drive housing 28 connects to the suction inlet 51.
  • the second cooling channel 64 is liquid-tightly connected to the annular space outlet 34.
  • From the pump to be conveyed liquid can thus first from the supply line 61, the first cooling passage 62 and then flow through the annulus 32, and then pass through the connecting line 63 to the suction inlet 51 so that they are pressurized by the pump 12 and on the Pressure outlet 52 can be discharged.
  • the two cooling channels 62 and 64 are integrally connected via heat conducting ribs 66 to a base body 68 of the drive housing 28.
  • the main body 68 surrounds the swash plate 56 and also forms the bearing plate 26.
  • the drive housing 28 is made of metal, preferably of an aluminum alloy.
  • the motor pump unit 10 is characterized by a long service life.
  • Strömungsleitrippen 36 ensure that the liquid flows through the annulus 32 largely labyrinth-like, so that a very good heat transfer from the motor housing 17 is ensured to the liquid. Only a small portion of the liquid flows directly through the gaps 37 between the Strömungsleitrippen 36 and the motor housing 17 therethrough. Waste heat of the electric motor 11 can thus be reliably dissipated, wherein also the long-term water impermeability of the motor housing 17 is ensured. Also in the axial direction, the liquid can not flow out of the annular space 32. This is ensured by the provision of the radially loaded sealing rings 41 and 42. Since, in addition, the drive housing 28 is cooled by the liquid to be conveyed, overall the heat load of the motor pump unit 10 can be kept permanently low.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)

Description

Die Erfindung betrifft eine Motorpumpeneinheit für ein Hochdruckreinigungsgerät mit einem flüssigkeitsgekühlten Elektromotor und einer Pumpe, wobei der Elektromotor ein Motorgehäuse aufweist, das unter Ausbildung eines mit einem Ringraumeinlass und einem Ringraumauslass versehenen Ringraumes von einem zylindermantelförmigen Kühlgehäuse umgeben ist, und wobei die Pumpe einen mit dem Ringraumauslass verbundenen Saugeinlass zum Ansaugen von Flüssigkeit und einen Druckauslass zum Abgeben von Flüssigkeit aufweist und wobei die von der Pumpe zu fördernde Flüssigkeit dem Ringraumeinlass zuführbar ist und das Kühlgehäuse innenseitig mindestens eine Strömungsleitrippe umfasst zur Führung der Flüssigkeit im Ringraum.The invention relates to a motor pump unit for a high-pressure cleaning device having a liquid-cooled electric motor and a pump, wherein the electric motor has a motor housing which is surrounded by a cylinder jacket-shaped cooling housing to form an annulus provided with an annular space inlet and an annular space, and wherein the pump with the annular space connected suction inlet for sucking liquid and a pressure outlet for dispensing liquid and wherein the pumped by the pump liquid to be fed to the annular space inlet and the cooling housing inside at least one flow guide rib for guiding the liquid in the annular space.

Derartige Motorpumpeneinheiten sind aus der DE 10 2007 009 394 A1 bekannt. Sie kommen bei Hochdruckreinigungsgeräten zum Einsatz, bei denen eine Flüssigkeit, vorzugsweise Wasser, unter Druck gesetzt und anschließend über den Druckauslass abgegeben werden kann. An den Druckauslass kann ein Hochdruckschlauch angeschlossen werden, der an seinem freien Ende beispielsweise eine Sprühlanze trägt. Dies gibt die Möglichkeit, einen unter Hochdruck stehenden Flüssigkeitsstrahl auf einen Gegenstand zu richten, beispielsweise um den Gegenstand zu reinigen.Such motor pump units are from the DE 10 2007 009 394 A1 known. They are used in high-pressure cleaning devices in which a liquid, preferably water, can be pressurized and then discharged via the pressure outlet. At the pressure outlet, a high-pressure hose can be connected, which carries at its free end, for example, a spray lance. This provides the ability to direct a high pressure jet of liquid at an object, for example, to clean the object.

Der Antrieb der Pumpe erfolgt mittels eines Elektromotors, der von der Flüssigkeit gekühlt wird, die der Pumpe zugeführt wird. Hierzu ist das Motorgehäuse von einem zylindermantelförmigen Kühlgehäuse umgeben, wobei zwischen dem Motorgehäuse und dem Kühlgehäuse ein Ringraum ausgebildet ist, dem über einen Ringraumeinlass von der Pumpe zu fördernde Flüssigkeit zugeführt werden kann. Die Flüssigkeit kann den Ringraum durchströmen und über den Ringraumauslass zum Saugeinlass der Pumpe gelangen, so dass sie anschließend unter Druck gesetzt werden kann. Strömungsleitelemente in Form von Strömungsleitrippen, die innenseitig am Kühlgehäuse angeordnet sind, führen die Flüssigkeit durch den Ringraum hindurch. Die Strömungsleitrippen sind bei der Motorpumpeneinheit, die in der DE 10 2007 009 394 A1 beschrieben wird, als Stützrippen ausgestaltet, mit deren Hilfe sich das Kühlgehäuse am Motorgehäuse abstützt.The drive of the pump by means of an electric motor, which is cooled by the liquid which is supplied to the pump. For this purpose, the motor housing is surrounded by a cylinder jacket-shaped cooling housing, wherein an annular space is formed between the motor housing and the cooling housing, which can be supplied via an annulus inlet of the pump to be pumped liquid. The liquid can flow through the annular space and pass through the annular space outlet to the suction inlet of the pump so that it can then be pressurized. Flow guide in the form of Strömungsleitrippen, which are arranged on the inside of the cooling housing, pass the liquid through the annulus. The Strömungsleitrippen are in the motor pump unit, which in the DE 10 2007 009 394 A1 is described, designed as support ribs, with the help of which the cooling housing is supported on the motor housing.

In vielen Fällen wird die Pumpe an das öffentliche Wasserversorgungsnetz angeschlossen. Dies hat zur Folge, dass innerhalb des Ringraums der im Wasserversorgungsnetz herrschende Förderdruck von einigen bar, beispielsweise 5 bis 10 bar, herrscht. Für die Funktionsfähigkeit der Motorpumpeneinheit ist es erforderlich, dass der Ringraum zuverlässig abgedichtet ist, insbesondere ist dafür Sorge zu tragen, dass auch das Motorgehäuse langfristig wasserundurchlässig ist.In many cases, the pump will be connected to the public water supply network. This has the consequence that within the annular space prevailing in the water supply network discharge pressure of a few bar, for example, 5 to 10 bar, prevails. For the operability of the motor pump unit, it is necessary that the annulus is reliably sealed, in particular, it must be ensured that the motor housing is water impermeable in the long term.

Aufgabe der vorliegenden Erfindung ist es, eine Motorpumpeneinheit der eingangs genannten Art derart weiterzubilden, dass sichergestellt ist, dass auch langfristig keine Flüssigkeit aus dem Ringraum heraustreten kann.Object of the present invention is to develop a motor pump unit of the type mentioned in such a way that it is ensured that even in the long term no liquid can escape from the annulus.

Diese Aufgabe wird bei einer Motorpumpeneinheit der gattungsgemäßen Art erfindungsgemäß dadurch gelöst, dass die mindestens eine Strömungsleitrippe zum Motorgehäuse beabstandet ist.This object is achieved in a motor pump unit of the generic type according to the invention in that the at least one Strömungsleitrippe is spaced from the motor housing.

Während des Betriebs unterliegt das Motorgehäuse unvermeidbaren Vibrationen. Diese können zu einer Relativbewegung zwischen den Strömungsleitrippen des Kühlgehäuses und dem Motorgehäuse führen. Liegen die Strömungsleitrippen unmittelbar am Motorgehäuse an, so können die Strömungsleitrippen die Oberfläche des Motorgehäuses durch Scheuern oder Kratzen beschädigen. Dadurch kann die Oberflächenstruktur des Motorgehäuses beeinträchtigt werden, und dies wiederum kann dazu führen, dass Flüssigkeit aus dem Ringraum durch das beschädigte Motorgehäuse hindurch in das Innere des Elektromotors eintreten kann. Um einer solchen Beeinträchtigung der Wasserundurchlässigkeit des Motorgehäuses entgegenzuwirken, ist erfindungsgemäß vorgesehen, dass die Strömungsleitrippen einen Abstand zum Motorgehäuse einnehmen, das heißt zwischen den Strömungsleitrippen und dem Motorgehäuse erstreckt sich ein Spalt. Überraschenderweise hat sich gezeigt, dass trotz des Abstands zwischen dem Motorgehäuse und den Strömungsleitrippen die Flüssigkeit größtenteils mit definierter Richtung durch den Ringraum hindurchgeführt werden kann. Ein Großteil der Flüssigkeit strömt an den Strömungsleitrippen entlang, so dass die Flüssigkeitsströmung eine definierte Richtung innerhalb des Ringraumes einnimmt. Nur ein kleinerer Teil der Flüssigkeit strömt schräg oder quer zu den Strömungsleitrippen durch den Spalt zwischen den Strömungsleitrippen und dem Motorgehäuse hindurch. Die Bereitstellung eines Spalts zwischen den Strömungsleitrippen und dem Motorgehäuse stellt somit sicher, dass das Motorgehäuse dauerhaft wasserundurchlässig bleibt, und dennoch kann die Flüssigkeit zur Kühlung des Elektromotors zuverlässig durch den Ringraum hindurchgeführt werden.During operation, the motor housing is subject to unavoidable vibration. These can lead to a relative movement between the flow guide ribs of the cooling housing and the motor housing. If the flow guide ribs lie directly against the motor housing, the flow guide ribs can damage the surface of the motor housing by rubbing or scratching. As a result, the surface structure of the motor housing can be affected, and this in turn can cause liquid from the annulus through the damaged motor housing can enter into the interior of the electric motor. In order to counteract such an impairment of the water impermeability of the motor housing, the invention provides that the Strömungsleitrippen occupy a distance from the motor housing, that is, between the Strömungsleitrippen and the motor housing, a gap extends. Surprisingly, it has been found that, in spite of the distance between the motor housing and the flow guide ribs, the fluid can largely be passed through the annular space with a defined direction. A large part of the liquid flows along the flow guide ribs, so that the liquid flow assumes a defined direction within the annular space. Only a minor part of the liquid flows obliquely or transversely to the flow guide ribs through the gap between the flow guide ribs and the motor housing. The provision of a gap between the Strömungsleitrippen and the motor housing thus ensures that the motor housing remains permanently impermeable to water, and yet the liquid for cooling the electric motor can be reliably passed through the annulus.

Von Vorteil ist es, wenn zwischen dem Ringraumeinlass und dem Ringraumauslass eine Strömungsleitrippe angeordnet ist. Diese stellt sicher, dass über den Ringraumeinlass in den Ringraum eintretende Flüssigkeit nicht unmittelbar zum Ringraumauslass gelangen kann, vielmehr umströmt ein Großteil der Flüssigkeit ausgehend vom Ringraumeinlass das gesamte Motorgehäuse, um erst dann zum Ringraumauslass zu gelangen.It is advantageous if a flow guide rib is arranged between the annular space inlet and the annular space outlet. This ensures that over The liquid entering the annular space can not directly reach the annular space outlet, but much of the liquid, starting from the annular space inlet, flows around the entire motor housing, only then to reach the annular space outlet.

Es kann beispielsweise vorgesehen sein, dass das Kühlgehäuse mehrere, in Umfangsrichtung versetzt zueinander angeordnete Strömungsleitrippen aufweist, die jeweils einen Durchlass umfassen, wobei die Durchlässe benachbarter Strömungsleitrippen axial versetzt zueinander angeordnet sind. Bei einer derartigen Ausgestaltung definieren die Strömungsleitrippen insgesamt einen labyrinthartigen, in Umfangsrichtung um das Motorgehäuse herumführenden Strömungsweg vom Ringraumeinlass zum Ringraumauslass. Dies hat eine besonders wirksame Kühlung des Elektromotors zur Folge.It can be provided, for example, that the cooling housing has a plurality of circumferentially offset from one another arranged Strömungsleitrippen, each comprising a passage, wherein the passages of adjacent Strömungsleitrippen are axially offset from one another. In such an embodiment, the Strömungsleitrippen define a total of a labyrinth-like, in the circumferential direction around the motor housing leading around the flow path from the annular space inlet to the annulus outlet. This results in a particularly effective cooling of the electric motor result.

Die Höhe des Spalts zwischen der mindestens einen Strömungsleitrippe und dem Motorgehäuse beträgt bevorzugt mindestens 0,3 mm. Insbesondere eine Höhe von 0,5 mm und mehr hat sich als vorteilhaft erwiesen. Es kann beispielsweise vorgesehen sein, dass die Höhe des Spalts zwischen der mindestens einen Strömungsleitrippe und dem Motorgehäuse mindestens 1 mm beträgt.The height of the gap between the at least one flow guide rib and the motor housing is preferably at least 0.3 mm. In particular, a height of 0.5 mm and more has proved to be advantageous. It can be provided, for example, that the height of the gap between the at least one flow guide rib and the motor housing is at least 1 mm.

Die Höhe der Strömungsleitrippen beträgt bevorzugt mindestens 1 mm. Es kann beispielsweise vorgesehen sein, dass die Strömungsleitrippen eine Höhe von zumindest 2 mm aufweisen. Bei einer vorteilhaften Ausführungsform ist eine Höhe von mindestens 3 mm vorgesehen.The height of the Strömungsleitrippen is preferably at least 1 mm. It can be provided, for example, that the flow guide ribs have a height of at least 2 mm. In an advantageous embodiment, a height of at least 3 mm is provided.

Günstig ist es, wenn die Höhe der Strömungsleitrippen ein Mehrfaches der Höhe des Spalts beträgt.It is advantageous if the height of the flow guide ribs is a multiple of the height of the gap.

Um die Wasserundurchlässigkeit des Motorgehäuses zu steigern, ist bei einer vorteilhaften Ausführungsform vorgesehen, dass das Motorgehäuse eine Korrosionsschutzschicht trägt. Das Motorgehäuse kann zum Beispiel mit einem speziellen Schutzmaterial beschichtet sein. Es kann aber auch vorgesehen sein, dass die Korrosionsschutzschicht als Oxidationsschicht des Motorgehäuses ausgestaltet ist.In order to increase the water impermeability of the motor housing, it is provided in an advantageous embodiment that the motor housing carries a corrosion protection layer. The motor housing may, for example, be coated with a special protective material. But it can also be provided that the corrosion protection layer is designed as an oxidation layer of the motor housing.

Das Motorgehäuse kann bevorzugt aus einem Tiefziehstahl gefertigt sein, der oberflächlich oxidiert ist.The motor housing may preferably be made of a deep-drawn steel, which is oxidized on the surface.

Das Kühlgehäuse ist vorzugsweise aus Kunststoff gefertigt. Kunststoffgehäuse sind in der Regel vibrationsanfällig. Es ist daher gerade für Kunststoffgehäuse von besonderem Vorteil, wenn die mindestens eine Strömungsleitrippe einen Abstand zum Motorgehäuse einnimmt, um eine Oberflächenbeschädigung zu vermeiden.The cooling housing is preferably made of plastic. Plastic housings are usually prone to vibration. It is therefore particularly advantageous for plastic housings when the at least one flow guide rib is at a distance from the motor housing in order to avoid surface damage.

Es ist von Vorteil, wenn das zylindermantelförmige Kühlgehäuse in axialer Richtung auf das Motorgehäuse aufschiebbar ist. Dies vereinfacht die Montage der Motorpumpeneinheit.It is advantageous if the cylinder jacket-shaped cooling housing in the axial direction can be pushed onto the motor housing. This simplifies the assembly of the motor pump unit.

Um zu vermeiden, dass Flüssigkeit in axialer Richtung aus dem Ringraum heraustreten kann, ist der Ringraum bei einer besonders bevorzugten Ausführungsform mittels eines vorderen und eines hinteren Dichtrings abgedichtet, die in radialer Richtung zwischen das Motorgehäuse und das Kühlgehäuse eingeklemmt sind. Die Abdichtung des Ringraums im Bereich der Dichtringe erfolgt somit durch eine radiale Belastung der Dichtringe. Dies hat ebenfalls eine Vereinfachung der Montage der Motorpumpeneinheit zur Folge, denn die Dichtwirkung wird allein durch die radiale Beaufschlagung der O-Ringe sichergestellt, es sich nicht erforderlich, die O-Ringe in axialer Richtung zu verspannen.In order to avoid that liquid can emerge from the annular space in the axial direction, the annular space is sealed in a particularly preferred embodiment by means of a front and a rear sealing ring, which in the radial direction between the motor housing and the cooling housing are trapped. The sealing of the annular space in the region of the sealing rings is thus effected by a radial load of the sealing rings. This also has a simplification of the assembly of the motor pump unit result, because the sealing effect is ensured solely by the radial loading of the O-rings, it is not necessary to clamp the O-rings in the axial direction.

Bei einer vorteilhaften Ausführungsform weist das Motorgehäuse der Pumpe zugewandt einen nach außen abstehenden Ringflansch auf, an den sich eine ringförmige Dichtfläche anschließt, an der der vordere Dichtring anliegt. Der nach außen abstehende Ringflansch des Motorgehäuses kann zwischen einem Lagerschild, das von einem Antriebsgehäuse der Pumpe gebildet wird, und einer Stirnseite des Kühlgehäuses eingespannt sein. Auf der der Pumpe abgewandten Rückseite des nach außen abstehenden Ringflansches kann der vordere Dichtring positioniert sein, der in radialer Richtung zwischen einer an den Ringflansch anschließenden ringförmigen Dichtfläche des Motorgehäuses und einer korrespondierenden ringförmigen Dichtfläche des Kühlgehäuses eingespannt ist.In an advantageous embodiment, the motor housing facing the pump has an outwardly projecting annular flange, which is adjoined by an annular sealing surface against which the front sealing ring rests. The outwardly projecting annular flange of the motor housing can be clamped between a bearing plate, which is formed by a drive housing of the pump, and an end face of the cooling housing. On the rear side facing away from the pump of the outwardly projecting annular flange of the front sealing ring may be positioned, which is clamped in the radial direction between an adjoining the annular flange annular sealing surface of the motor housing and a corresponding annular sealing surface of the cooling housing.

Zur Abdichtung des Ringraums in seinem der Pumpe abgewandten rückwärtigen Bereich ist es von Vorteil, wenn das Motorgehäuse der Pumpe abgewandt einen zylindermantelförmigen Kragen aufweist, der unter Zwischenlage des hinteren Dichtrings von einem zylindermantelförmigen Ansatz des Kühlgehäuses umgeben ist. Der zylindermantelförmige Kragen des topfförmigen Motorgehäuses kann zwischen dem Boden und dem Mantel des Motorgehäuses verlaufen. Ein zylindermantelförmiger Ansatz des Kühlgehäuses kann konzentrisch zum zylindermantelförmigen Kragen des Motorgehäuses ausgerichtet sein, und zwischen dem Kragen und dem Ansatz kann der hintere Dichtring in radialer Richtung verspannt sein.For sealing the annular space in its rear region remote from the pump, it is advantageous if the motor housing facing away from the pump has a cylinder-jacket-shaped collar which is surrounded by a cylinder jacket-shaped projection of the cooling housing with the interposition of the rear sealing ring. The cylinder jacket-shaped collar of the pot-shaped motor housing can extend between the bottom and the jacket of the motor housing. A cylinder jacket-shaped projection of the cooling housing can be aligned concentrically with the cylinder jacket-shaped collar of the motor housing be, and between the collar and the neck of the rear sealing ring can be braced in the radial direction.

Die nachfolgende Beschreibung einer bevorzugten Ausführungsform der Erfindung dient im Zusammenhang mit der Zeichnung der näheren Erläuterung. Es zeigen:

Figur 1:
eine Teilschnittansicht einer Motorpumpeneinheit entlang der Linie 1-1 in Figur 3;
Figur 2:
eine Schnittansicht der Motorpumpeneinheit längs der Linie 2-2 in Figur 1 und
Figur 3:
eine Schnittansicht der Motorpumpeneinheit im Bereich eines Elektromotors quer zur Längsachse der Motorpumpeneinheit.
The following description of a preferred embodiment of the invention serves in conjunction with the drawings for further explanation. Show it:
FIG. 1:
a partial sectional view of a motor pump unit along the line 1-1 in FIG. 3 ;
FIG. 2:
a sectional view of the motor pump unit along the line 2-2 in FIG. 1 and
FIG. 3:
a sectional view of the motor pump unit in the region of an electric motor transverse to the longitudinal axis of the motor pump unit.

In der Zeichnung ist schematisch eine erfindungsgemäße Motorpumpeneinheit 10 dargestellt mit einem flüssigkeitsgekühlten Elektromotor 11 und einer Pumpe 12. Der Elektromotor 11 weist in üblicher Weise einen Rotor 14 auf, der von einem Stator 15 umgeben ist. An den Stator 15 schließt sich außenseitig ein topfförmiges Motorgehäuse 17 an, das aus einem Tiefziehstahl gefertigt ist. Es weist eine zylindermantelförmige Umfangswand 18 auf sowie einen Boden 19. Der Boden 19 bildet eine axial nach außen gerichtete Aufnahme 20 für ein erstes Lager 21 einer Motorwelle 22. Ein zweites Lager 23 für die Motorwelle 22 ist an einem Lagerschild 26 angeordnet, das von einem Antriebsgehäuse 28 der Pumpe 12 gebildet ist.In the drawing, a motor pump unit 10 according to the invention is shown schematically with a liquid-cooled electric motor 11 and a pump 12. The electric motor 11 has in the usual way a rotor 14 which is surrounded by a stator 15. On the stator 15, a pot-shaped motor housing 17 connects to the outside, which is made of a deep-drawn steel. It has a cylinder jacket-shaped peripheral wall 18 and a bottom 19. The bottom 19 forms an axially outwardly directed receptacle 20 for a first bearing 21 of a motor shaft 22. A second bearing 23 for the motor shaft 22 is disposed on a bearing plate 26, of a Drive housing 28 of the pump 12 is formed.

Das Motorgehäuse 17 ist in Umfangsrichtung von einem zylindermantelförmigen Kühlgehäuse 30 umgeben, wobei zwischen dem Motorgehäuse 17 und dem Kühlgehäuse 30 ein Ringraum 32 angeordnet ist, der das Motorgehäuse 17 in Umfangsrichtung vollständig umgibt. Über einen Ringraumeinlass 33 des Kühlgehäuses 30 kann dem Ringraum 32 Flüssigkeit zugeführt werden, die anschließend den Ringraum 32 durchströmt. Über einen Ringraumauslass 34 des Kühlgehäuses 30 kann die Flüssigkeit aus dem Ringraum 32 herausströmen.The motor housing 17 is surrounded in the circumferential direction by a cylinder jacket-shaped cooling housing 30, wherein between the motor housing 17 and the cooling housing 30, an annular space 32 is arranged, which completely surrounds the motor housing 17 in the circumferential direction. Via an annular space inlet 33 of the cooling housing 30, liquid can be supplied to the annular space 32, which then flows through the annular space 32. Via an annular space outlet 34 of the cooling housing 30, the liquid can flow out of the annular space 32.

Das Kühlgehäuse 30 trägt innenseitig mehrere in Umfangsrichtung in gleichmäßigem Abstand zueinander angeordnete Strömungsleitrippen 36, die radial in den Ringraum 32 hineinragen, wobei sie allerdings das Motorgehäuse 17 nicht berühren, vielmehr erstreckt sich zwischen jeder Strömungsleitrippe 36 und dem Motorgehäuse 17 ein Spalt 37 mit einer Höhe von etwa 1 mm. Die Höhe der Strömungsleitrippen 36 in radialer Richtung beträgt mindestens 2 mm. Es ist nämlich vorteilhaft, wenn die Höhe der Strömungsleitrippen 36 mindestens doppelt so groß ist wie die Höhe des Spalts 37. Von besonderem Vorteil ist es, wenn die Höhe der Strömungsleitrippen 36 in radialer Richtung ein Mehrfaches der Höhe des Spalts 37 trägt. Beispielsweise können die Strömungsleitrippen 36 eine Höhe von mindestens 3 mm aufweisen und die Höhe des Spalts 37 kann maximal 1 mm betragen.The cooling housing 30 carries on the inside a plurality of circumferentially uniformly spaced Strömungsleitrippen 36 which protrude radially into the annular space 32, but they do not touch the motor housing 17, but extends between each Strömungsleitrippe 36 and the motor housing 17, a gap 37 with a height of about 1 mm. The height of the Strömungsleitrippen 36 in the radial direction is at least 2 mm. It is advantageous if the height of the Strömungsleitrippen 36 is at least twice as large as the height of the gap 37. It is particularly advantageous if the height of the Strömungsleitrippen 36 in the radial direction a multiple of the height of the gap 37 carries. For example, the Strömungsleitrippen 36 have a height of at least 3 mm and the height of the gap 37 may be at most 1 mm.

Die Strömungsleitrippen 36 weisen jeweils einen Durchlass 38 auf, über den Flüssigkeit, die dem Ringraum 32 zugeführt wird, hindurchströmen kann. Die Durchlässe 38 benachbarter Strömungsleitrippen 36 sind axial versetzt zueinander angeordnet, so dass die Strömungsleitrippen 36 einen labyrinthartigen, in Umfangsrichtung um das Motorgehäuse 17 herumführenden Strömungsweg vom Ringraumeinlass 33 zum Ringraumauslass 34 definieren.The Strömungsleitrippen 36 each have a passage 38 through which liquid, which is supplied to the annular space 32, can flow therethrough. The passages 38 of adjacent Strömungsleitrippen 36 are axially offset from one another, so that the Strömungsleitrippen 36 a labyrinthine, in the circumferential direction around the motor housing 17 around leading flow path from the annulus inlet 33 to the annulus outlet 34 define.

In axialer Richtung wird der Ringraum 32 von einem vorderen Dichtring 41 und einem hinteren Dichtring 42 abgedichtet. Der vordere Dichtring 41 ist auf der der Pumpe 12 abgewandten Seite eines nach außen abstehenden Ringflanschs 44 des Motorgehäuses 17 angeordnet, der zwischen das Lagerschild 26 und die der Pumpe 12 zugewandte Stirnseite des Kühlgehäuses 30 eingespannt ist.In the axial direction, the annular space 32 is sealed by a front sealing ring 41 and a rear sealing ring 42. The front sealing ring 41 is arranged on the side facing away from the pump 12 of an outwardly projecting annular flange 44 of the motor housing 17, which is clamped between the bearing plate 26 and the pump 12 facing the end face of the cooling housing 30.

Die Abdichtung des Ringraums 32 im Bereich des vorderen Dichtrings 41 erfolgt durch radiale Belastung des Dichtrings 41. Dieser ist zwischen einer ringförmigen Dichtfläche 45 des Motorgehäuses 17 und einer korrespondierenden ringförmigen Dichtfläche 46 des Kühlgehäuses 30 in radialer Richtung verspannt.The sealing of the annular space 32 in the region of the front sealing ring 41 is effected by radial loading of the sealing ring 41. This is braced between an annular sealing surface 45 of the motor housing 17 and a corresponding annular sealing surface 46 of the cooling housing 30 in the radial direction.

Der hintere Dichtring 42 liegt an einem zylindermantelförmigen Kragen 48 des Motorgehäuses 17 an, der sich im Übergangsbereich zwischen dem Boden 19 und der Umfangswand 18 konzentrisch zur Motorwelle 22 erstreckt. Der Kragen 48 ist von einem zylindermantelförmigen Ansatz 49 des Kühlgehäuses 30 umgeben, der konzentrisch zum Kragen 48 ausgerichtet ist. Zwischen dem Kragen 48 und dem Ansatz 49 ist der hintere Dichtring 42 in radialer Richtung verspannt. In axialer Richtung wird er von einem radial nach innen gerichteten Rücksprung des Kühlgehäuses 30 abgestützt.The rear sealing ring 42 abuts against a cylinder jacket-shaped collar 48 of the motor housing 17, which extends in the transition region between the bottom 19 and the peripheral wall 18 concentric with the motor shaft 22. The collar 48 is surrounded by a cylinder jacket-shaped projection 49 of the cooling housing 30, which is aligned concentrically with the collar 48. Between the collar 48 and the projection 49 of the rear sealing ring 42 is braced in the radial direction. In the axial direction, it is supported by a radially inwardly directed return of the cooling housing 30.

Das Motorgehäuse 17 ist, darauf wurde bereits hingewiesen, aus einem Tiefziehstahl gefertigt. Dieser weist oberflächlich eine Oxidationsschicht auf, die als Korrosionsschutzschicht wirkt und sicherstellt, dass das Motorgehäuse 17 dauerhaft wasserundurchlässig ist. Da die Strömungsleitrippen 36 einen Abstand zum Motorgehäuse 17 einnehmen, ist sichergestellt, dass die oberflächliche Oxidationsschicht des Motorgehäuses 17 nicht durch Vibrationen des Motorgehäuses 17 beeinträchtigt wird, die eine Beschädigung der Oberfläche des Motorgehäuses 17 zur Folge haben könnten, falls die Strömungsleitrippen 36 die Oberfläche des Motorgehäuses 17 berühren könnten.The motor housing 17 is, it has already been noted, made of a deep-drawing steel. This has superficially on an oxidation layer, the acts as a corrosion protection layer and ensures that the motor housing 17 is permanently impermeable to water. Since the Strömungsleitrippen 36 occupy a distance from the motor housing 17, it is ensured that the superficial oxidation layer of the motor housing 17 is not affected by vibrations of the motor housing 17, which could result in damage to the surface of the motor housing 17, if the Strömungsleitrippen 36, the surface of the Motor housing 17 could touch.

Die Pumpe 12 weist in üblicher Weise einen Saugeinlass 51 und einen Druckauslass 52 auf. Parallel zur Motorwelle 22 ausgerichtete Kolben 54 der Pumpe 12 liegen an einer Taumelscheibe 56 an, die im Antriebsgehäuse 28, dem Lagerschild 26 benachbart, angeordnet und mit der Motorwelle 22 gekoppelt ist. Lediglich zur Erzielung einer besseren Übersicht sind die Kolben 54 in der Zeichnung in einem Abstand zur Taumelscheibe 56 dargestellt. Tatsächlich liegen sie stirnseitig an der Taumelscheibe 56 an und werden dadurch zu einer hin- und hergehenden Bewegung angetrieben. Mit ihrem der Taumelscheibe 56 abgewandten Ende tauchen die Kolben 54 in üblicher Weise jeweils in einen Pumpraum ein, so dass vom Saugeinlass 51 Flüssigkeit in den Pumpraum eingesaugt und unter Druck über den Druckauslass 52 abgegeben werden kann.The pump 12 has a suction inlet 51 and a pressure outlet 52 in the usual way. Parallel to the motor shaft 22 aligned piston 54 of the pump 12 are applied to a swash plate 56 which is adjacent to the drive housing 28, the bearing plate 26, and coupled to the motor shaft 22. Only to achieve a better overview, the piston 54 are shown in the drawing at a distance from the swash plate 56. In fact, they bear against the swash plate 56 on the face side and are thereby driven to a reciprocating motion. With their end facing away from the swash plate 56, the pistons 54 dive into a pumping space in the usual way, so that liquid can be sucked into the pumping space from the suction inlet 51 and released under pressure via the pressure outlet 52.

Die Zuführung von Flüssigkeit zur Pumpe 12 erfolgt über eine Leitungsanordnung 60. Dies wird insbesondere aus Figur 2 deutlich. Die Leitungsanordnung 60 umfasst eine Zufuhrleitung 61, die an einen ersten Kühlkanal 62 des Antriebsgehäuses 28 angeschlossen ist, der wiederum flüssigkeitsdicht mit dem Ringraumeinlass 33 verbunden ist. Die Leitungsanordnung 60 weist außerdem eine Verbindungsleitung 63 auf, die parallel zur Zufuhrleitung 61 ausgerichtet ist und einen parallel zum ersten Kühlkanal 62 ausgerichteten zweiten Kühlkanal 64 des Antriebsgehäuses 28 mit dem Saugeinlass 51 verbindet. Der zweite Kühlkanal 64 ist flüssigkeitsdicht mit dem Ringraumauslass 34 verbunden. Von der Pumpe zu fördernde Flüssigkeit kann somit ausgehend von der Zufuhrleitung 61 zunächst den ersten Kühlkanal 62 und anschließend den Ringraum 32 durchströmen, um dann über die Verbindungsleitung 63 zum Saugeinlass 51 zu gelangen, so dass sie von der Pumpe 12 unter Druck gesetzt und über den Druckauslass 52 abgegeben werden kann.The supply of liquid to the pump 12 via a line arrangement 60. This is in particular from FIG. 2 clear. The conduit arrangement 60 comprises a supply line 61, which is connected to a first cooling channel 62 of the drive housing 28, which in turn is connected in a liquid-tight manner to the annular space inlet 33. The conduit arrangement 60 also has a connection line 63, which is aligned parallel to the supply line 61 and a parallel to the first cooling channel 62 aligned second cooling channel 64 of the drive housing 28 connects to the suction inlet 51. The second cooling channel 64 is liquid-tightly connected to the annular space outlet 34. From the pump to be conveyed liquid can thus first from the supply line 61, the first cooling passage 62 and then flow through the annulus 32, and then pass through the connecting line 63 to the suction inlet 51 so that they are pressurized by the pump 12 and on the Pressure outlet 52 can be discharged.

Die beiden Kühlkanäle 62 und 64 sind über Wärmeleitrippen 66 einstückig mit einem Grundkörper 68 des Antriebsgehäuses 28 verbunden. Der Grundkörper 68 umgibt die Taumelscheibe 56 und bildet auch das Lagerschild 26 aus. Das Antriebsgehäuse 28 ist aus Metall gefertigt, vorzugsweise aus einer Aluminiumlegierung. Durch die Bereitstellung der Kühlkanäle 62 und 64 kann es ebenso wie der Elektromotor 11 von der zu fördernden Flüssigkeit gekühlt werden. Dies erhöht die Lebensdauer der Motorpumpeneinheit 10, insbesondere ist sichergestellt, dass sich das zweite Lager 23, das Lagerschild 26 und die Taumelscheibe 56 sowie auch die Kolben 54 und eine Kolbenführung, in der sie linear verschiebbar gelagert sind, nicht überhitzen.The two cooling channels 62 and 64 are integrally connected via heat conducting ribs 66 to a base body 68 of the drive housing 28. The main body 68 surrounds the swash plate 56 and also forms the bearing plate 26. The drive housing 28 is made of metal, preferably of an aluminum alloy. By providing the cooling channels 62 and 64, it can be cooled as well as the electric motor 11 of the liquid to be delivered. This increases the service life of the motor pump unit 10, in particular ensures that the second bearing 23, the bearing plate 26 and the swash plate 56 and the piston 54 and a piston guide in which they are mounted linearly displaceable, not overheat.

Insgesamt zeichnet sich somit die erfindungsgemäße Motorpumpeneinheit 10 durch eine hohe Lebensdauer aus. Die im Abstand zum Motorgehäuse 17 angeordnete Strömungsleitrippen 36 stellen sicher, dass die Flüssigkeit den Ringraum 32 größtenteils labyrinthartig durchströmt, so dass ein sehr guter Wärmeübergang vom Motorgehäuse 17 zu der Flüssigkeit sichergestellt ist. Nur ein kleiner Teil der Flüssigkeit strömt unmittelbar durch die Spalte 37 zwischen den Strömungsleitrippen 36 und dem Motorgehäuse 17 hindurch. Abwärme des Elektromotors 11 kann somit zuverlässig abgeführt werden, wobei auch langfristig die Wasserundurchlässigkeit des Motorgehäuses 17 sichergestellt ist. Auch in axialer Richtung kann die Flüssigkeit nicht aus dem Ringraum 32 herausströmen. Dies wird durch die Bereitstellung der in radialer Richtung belasteten Dichtringe 41 und 42 sichergestellt. Da ergänzend auch das Antriebsgehäuse 28 von der zu fördernden Flüssigkeit gekühlt wird, kann insgesamt die Wärmebelastung der Motorpumpeneinheit 10 dauerhaft gering gehalten werden.Overall, therefore, the motor pump unit 10 according to the invention is characterized by a long service life. The arranged at a distance from the motor housing 17 Strömungsleitrippen 36 ensure that the liquid flows through the annulus 32 largely labyrinth-like, so that a very good heat transfer from the motor housing 17 is ensured to the liquid. Only a small portion of the liquid flows directly through the gaps 37 between the Strömungsleitrippen 36 and the motor housing 17 therethrough. Waste heat of the electric motor 11 can thus be reliably dissipated, wherein also the long-term water impermeability of the motor housing 17 is ensured. Also in the axial direction, the liquid can not flow out of the annular space 32. This is ensured by the provision of the radially loaded sealing rings 41 and 42. Since, in addition, the drive housing 28 is cooled by the liquid to be conveyed, overall the heat load of the motor pump unit 10 can be kept permanently low.

Claims (8)

  1. Motor pump unit (10) for a high-pressure cleaning apparatus having a liquid-cooled electric motor (11) and a pump (12), wherein the electric motor (11) has a motor housing (17) that is surrounded by a cylindrical shell shaped cooling housing (30) with an annular space (32) having an annular space inlet (33) and an annular space outlet (34) formed therebetween, and wherein the pump (12) has a suction inlet (51) connected to the annular space outlet (34) for drawing in liquid and a pressure outlet (52) for discharging liquid, and wherein the liquid to be transported by the pump (12) is suppliable to the annular space inlet (33) and wherein the cooling housing (30), on its inside, comprises at least one flow guide rib (36) for guiding the liquid within the annular space (32), characterized in that the at least one flow guide rib (36) is spaced-apart from the motor housing (17).
  2. Motor pump unit in accordance with claim 1, characterized in that a flow guide rib (36) is arranged between the annular space inlet (33) and the annular space outlet (34).
  3. Motor pump unit in accordance with claim 1 or 2, characterized in that a gap (37) having a height of at least 0.3 mm is arranged between the at least one flow guide rib (36) and the motor housing (17).
  4. Motor pump unit in accordance with any one of the preceding claims, characterized in that the motor housing (17) has a corrosion-protective layer.
  5. Motor pump unit in accordance with claim 4, characterized in that the corrosion-protective layer is configured as an oxidation layer.
  6. Motor pump unit in accordance with any one of the preceding claims, characterized in that the annular space (32) is sealed by means of a front and a rear sealing ring (41, 42) which are each clamped in a radial direction between the motor housing (17) and the cooling housing (30).
  7. Motor pump unit in accordance with claim 6, characterized in that the motor housing (17), on the side facing towards the pump (12), has an outward-projecting annular flange (44) which is followed by an annular sealing face (45) contacted by the front sealing ring (41).
  8. Motor pump unit in accordance with claim 6 or 7, characterized in that the motor housing (17), on the side facing away from the pump (12), has a cylindrical shell shaped collar (48) which is surrounded by a cylindrical shell shaped projection (49) of the cooling housing (30) with the rear sealing ring (42) interposed therebetween.
EP09776377.5A 2009-02-13 2009-02-13 Motor pump unit Active EP2396550B1 (en)

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2692358T3 (en) * 2010-12-14 2018-12-03 Alfred Kärcher SE & Co. KG Pump motor unit for a high-pressure cleaning device as well as a high-pressure cleaning device
CN105317692A (en) * 2014-05-30 2016-02-10 戴博邦浦股份有限公司 Motor casing for pumps, particularly centrifugal pumps and peripheral centrifugal pumps
US9946564B2 (en) 2015-06-23 2018-04-17 International Business Machines Corporation Adjusting virtual machine migration plans based on alert conditions related to future migrations

Family Cites Families (108)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2734459A (en) 1956-02-14 zimsky
US1431907A (en) * 1919-08-21 1922-10-10 Stanley S Cramer Pneumatic power generator
US1614091A (en) * 1925-01-12 1927-01-11 Ernest Van Toff Fan and fan blower
US2037245A (en) 1934-11-07 1936-04-14 Frank J Leifheit Fluid separator
US2301063A (en) 1941-07-12 1942-11-03 Ingersoll Rand Co Pumping mechanism
DE926676C (en) 1950-06-15 1955-04-21 Alwin Karl Dipl-Ing Borchers Electric machine
US2763214A (en) * 1953-12-17 1956-09-18 Howard T White Motor driven pumps
US2782720A (en) 1954-10-29 1957-02-26 Gen Electric Submersible pump-motor
US2913988A (en) * 1956-04-06 1959-11-24 Fostoria Corp Motor driven pumps
US2914253A (en) 1956-05-25 1959-11-24 Continental Can Co Means for maintaining constant delivery from a fluid circuit
US2854595A (en) * 1957-08-08 1958-09-30 Reda Pump Company Motor protector and cooling system for submergible pumping assembly
US2993449A (en) * 1959-03-09 1961-07-25 Hydratomic Engineering Corp Motor-pump
US3135213A (en) * 1962-10-30 1964-06-02 Watt V Smith Immersible motor-pump unit
SE367465B (en) * 1965-04-30 1974-05-27 Stenberg Flygt Ab
US3426691A (en) 1967-04-04 1969-02-11 Du Pont Pump expansion chamber
US3525001A (en) * 1968-09-23 1970-08-18 Preco Inc Liquid cooled electric motor
DE1964474A1 (en) * 1969-12-23 1971-07-15 Siemen & Hinsch Gmbh Pump for pumping media with high temperatures
US3667870A (en) * 1971-01-04 1972-06-06 Matsushita Electric Ind Co Ltd Motor driven pump
US3744935A (en) 1971-10-07 1973-07-10 Crane Co Cooling systems for motor driven pumps and the like
DE2413691B2 (en) * 1974-03-21 1976-04-29 PRESSURE OIL PUMP
JPS5131103A (en) 1974-09-10 1976-03-17 Kiichi Sekiguchi Kaarajioryodoraibuinshiataonkyo no zatsuonboshisochi
GB1547393A (en) 1976-04-15 1979-06-20 Sabev T Squrrel cage rotor electrical machines
DE2920883A1 (en) 1979-05-23 1980-12-04 Heinz Dipl Phys Bohn Heat-sink absorbing heat from field windings - has heat conductive medium in toroidal gap between pot inside larger pot
DE3001571C2 (en) 1980-01-17 1982-10-28 Alfred Kärcher GmbH & Co, 7057 Winnenden High pressure cleaning device
DE3017117A1 (en) 1980-05-03 1981-11-19 Alfred Kärcher GmbH & Co, 7057 Winnenden High pressure cleaner for multiple toilet units - has high pressure pump driven by electric motor and enclosed by housing made as two shells
DE3115698C1 (en) * 1981-04-18 1982-12-16 Alfred Kärcher GmbH & Co, 7057 Winnenden Motor pump unit for a high pressure cleaning device
DE8111792U1 (en) 1981-04-18 1981-08-27 Alfred Kärcher GmbH & Co, 7057 Winnenden "ENGINE PUMP UNIT FOR A HIGH PRESSURE CLEANING DEVICE"
JPS5958197A (en) * 1982-09-28 1984-04-03 Nikkiso Co Ltd Canned motor pump
DE3312828A1 (en) * 1983-04-09 1984-10-11 Flutec Fluidtechnische Geräte GmbH, 6603 Sulzbach DEVICE FOR CONVEYING A PRESSURE, IN PARTICULAR OIL
US4516044A (en) 1984-05-31 1985-05-07 Cincinnati Milacron Inc. Heat exchange apparatus for electric motor and electric motor equipped therewith
JPS619566A (en) 1984-06-21 1986-01-17 Yanmar Diesel Engine Co Ltd Beam explosion thermal spraying method for bottomed cylindrical body
DK481284A (en) 1984-10-08 1986-04-09 Knud Erik Westergaard ENGINE PUMP UNIT FOR A HIGH PRESSURE CLEANER
JPS61110877A (en) 1984-11-02 1986-05-29 Hitachi Ltd Vacuum pump for condenser
IT209469Z2 (en) * 1985-07-09 1988-10-10 Lafert Srl FORCED ELECTRIC MOTOR FORCED WITH LIQUID.
US4958988A (en) * 1985-09-26 1990-09-25 Ormat Turbines, Ltd. Motor driven pump for pumping viscous solutions
DE3534665A1 (en) 1985-09-28 1987-04-09 Bosch Gmbh Robert Two-position solenoid valve
DE3545665A1 (en) * 1985-12-21 1987-07-02 Kaercher Gmbh & Co Alfred Liquid-cooled electric motor
DE8536175U1 (en) 1986-02-05 1987-07-02 Alfred Kärcher GmbH & Co, 7057 Winnenden Liquid-cooled electric motor
JPS63257434A (en) 1987-04-13 1988-10-25 Mitsubishi Electric Corp Ac generator for rolling stock
US4934914A (en) * 1987-07-30 1990-06-19 Ebara Corporation Portable motor pump
DE3862268D1 (en) * 1987-09-15 1991-05-08 Bieri Pumpenbau Ag CIRCUIT PUMP, IN PARTICULAR FOR HOT WATER SYSTEMS.
DE3736159C3 (en) * 1987-10-26 1993-09-30 Abs Pumpen Ag Electric motor
DE3738592C1 (en) * 1987-11-13 1989-05-24 Licentia Gmbh Electric motor for driving a liquid pump, and a method for its production
US4844701A (en) 1987-12-02 1989-07-04 The Gorman-Rupp Company Mobile pump apparatus
JPH0810974B2 (en) 1988-04-25 1996-01-31 三菱電機株式会社 Vehicle alternator
DE3817641A1 (en) 1988-05-25 1989-11-30 Kaercher Gmbh & Co Alfred HIGH PRESSURE CLEANER
JPH0213135A (en) 1988-06-30 1990-01-17 Sony Corp Digital signal transmission equipment
US5040950A (en) * 1989-08-07 1991-08-20 Northland Aluminum Products, Inc. Power washing apparatus
JP2522835B2 (en) 1989-08-31 1996-08-07 富士写真フイルム株式会社 Photosensitive material processing equipment
JP2820463B2 (en) 1989-11-02 1998-11-05 松下電器産業株式会社 How to start the scroll compressor
DE4017193A1 (en) 1990-05-29 1991-12-05 Leybold Ag LOW-NOISE VACUUM PUMP
DE4105349A1 (en) * 1991-02-21 1992-08-27 Swf Auto Electric Gmbh ELECTRIC MOTOR WITH PUMP ON
SE9102517L (en) * 1991-09-03 1992-09-07 Flygt Ab Itt DEVICE FOR ASTADCOMMATING BY COOLING A CHEATED CHEATED ELECTRICAL ENGINE
US5240391A (en) 1992-05-21 1993-08-31 Carrier Corporation Compressor suction inlet duct
JP3207253B2 (en) 1992-06-30 2001-09-10 三信工業株式会社 Cowling structure for ship propulsion
US5283915A (en) 1992-08-10 1994-02-08 Softub, Inc. Power package for spa apparatus
DE4301666A1 (en) 1993-01-22 1994-07-28 Pierburg Gmbh Electrically powered air pump
US5350281A (en) * 1993-01-26 1994-09-27 Sundstrand Corporation Fan with secondary air passage for motor cooling
IT229678Y1 (en) 1993-02-26 1999-01-29 Gallone Cesare PROTECTION DEVICE AGAINST SPRAYS OF WATER FOR ELECTRIC SWITCHES AND SIMILAR
US5363674A (en) * 1993-05-04 1994-11-15 Ecoair Corp. Zero superheat refrigeration compression system
US5354182A (en) 1993-05-17 1994-10-11 Vickers, Incorporated Unitary electric-motor/hydraulic-pump assembly with noise reduction features
IT231077Y1 (en) 1993-12-22 1999-07-12 Pavarini Srl PRESSURE WASHER.
JP3014909B2 (en) 1993-12-27 2000-02-28 株式会社デンソー Scroll compressor
US5616973A (en) * 1994-06-29 1997-04-01 Yeomans Chicago Corporation Pump motor housing with improved cooling means
DE4445521C1 (en) 1994-12-20 1995-12-07 Kaercher Gmbh & Co Alfred Pump for high=pressure cleaning device
JP3281752B2 (en) 1995-03-30 2002-05-13 三菱重工業株式会社 Scroll type fluid machine
US5533875A (en) 1995-04-07 1996-07-09 American Standard Inc. Scroll compressor having a frame and open sleeve for controlling gas and lubricant flow
JPH0914199A (en) 1995-06-30 1997-01-14 Sugino Mach Ltd High pressure water generating device
JPH11509902A (en) 1995-07-31 1999-08-31 クノル−ブレムゼ ジステーメ フューア シーネンファールツォイゲ ゲゼルシャフト ミット ベシュレンクテル ハフツング Scroll type compressor used to generate compressed air especially for rail vehicles
DE19604447C2 (en) 1995-07-31 2002-03-21 Knorr Bremse Systeme scroll compressor
DE19652706A1 (en) 1995-12-22 1997-06-26 Rexroth Mannesmann Gmbh Compact hydraulic unit with hydro-pump driven by air-cooled electric motor
JP3737198B2 (en) 1996-04-25 2006-01-18 株式会社荏原製作所 Liquid supply device with soundproofing device
DE19628781A1 (en) 1996-07-17 1998-01-22 Voith Turbo Kg Pump unit with a drive cooling system using the liquid to be pumped
US5938389A (en) 1996-08-02 1999-08-17 Crown Cork & Seal Technologies Corporation Metal can and method of making
DE19716758C2 (en) 1997-04-12 2002-01-10 System Antriebstechnik Dresden Housing-free electrical machine with several axial cooling channels with direct fluid flow
JPH10317964A (en) 1997-05-15 1998-12-02 Hitachi Constr Mach Co Ltd Cooling device for engine of construction machine
JP3957365B2 (en) 1997-07-03 2007-08-15 北越工業株式会社 Soundproof structure of work equipment
JP3800374B2 (en) 1997-08-07 2006-07-26 本田技研工業株式会社 Engine generator
US5997261A (en) * 1997-10-31 1999-12-07 Siemens Canada Limited Pump motor having fluid cooling system
US6000917A (en) 1997-11-06 1999-12-14 American Standard Inc. Control of suction gas and lubricant flow in a scroll compressor
US6068459A (en) 1998-02-19 2000-05-30 Varian, Inc. Tip seal for scroll-type vacuum pump
DE19808602C1 (en) * 1998-02-28 1999-09-02 Grundfos As Device for external cooling of the electric drive motor of a centrifugal pump unit
JPH11270885A (en) 1998-03-24 1999-10-05 Mitsubishi Electric Corp Ventilator
EP0987441B1 (en) * 1998-09-15 2003-12-10 Wilo Ag Tube pump
EP0989658A1 (en) * 1998-09-28 2000-03-29 The Swatch Group Management Services AG Liquid-cooled aynchronous electric machine
JP2000130800A (en) 1998-10-29 2000-05-12 Sharp Corp Outdoor machine for air conditioner
US6132183A (en) 1998-11-23 2000-10-17 Carrier Corporation Compressor mounting
US6074185A (en) 1998-11-27 2000-06-13 General Motors Corporation Scroll compressor with improved tip seal
US6300693B1 (en) * 1999-03-05 2001-10-09 Emerson Electric Co. Electric motor cooling jacket assembly and method of manufacture
DE19910460A1 (en) 1999-03-10 2000-09-21 Bitzer Kuehlmaschinenbau Gmbh compressor
DE10045424A1 (en) 2000-09-14 2002-03-28 Va Tech Elin Ebg Motoren Gmbh Liquid-cooled electric motor
DE10065821A1 (en) 2000-12-22 2002-07-11 Bitzer Kuehlmaschinenbau Gmbh compressor
JP2003193837A (en) 2001-12-25 2003-07-09 Yanmar Co Ltd Power generation device
JP4099335B2 (en) 2002-02-12 2008-06-11 シスメックス株式会社 Air pump device
US7063519B2 (en) 2002-07-02 2006-06-20 R & D Dynamics Corporation Motor driven centrifugal compressor/blower
DE10247310A1 (en) 2002-10-10 2004-04-22 Siemens Ag Air-cooled electrical machine e.g. electric locomotive motor, uses single cooling fan for providing primary and secondary cooling air flows
JP2004183605A (en) 2002-12-05 2004-07-02 Sanden Corp Electric compressor
DE10305812A1 (en) 2003-02-12 2004-09-02 DMT GmbH Feinwerktechnische Komplettlösungen High pressure cleaning unit, to deliver a fluid, has a high pressure liquid-cooled pump embedded in a filling material in a housing fitted with supply lines
DE10307813B4 (en) 2003-02-24 2006-05-24 Siemens Ag Electric machine
US7182583B2 (en) 2004-02-06 2007-02-27 Sauer-Danfoss Inc. Electro-hydraulic power unit with a rotary cam hydraulic power unit
JP2005306153A (en) 2004-04-20 2005-11-04 Shin Caterpillar Mitsubishi Ltd Engine room structure of construction machine
JP2006291744A (en) 2005-04-06 2006-10-26 Denyo Co Ltd Engine driven working machine
JP4359265B2 (en) 2005-06-23 2009-11-04 本田技研工業株式会社 General-purpose engine muffler cover structure
DE102005046120A1 (en) 2005-09-26 2007-03-29 Wilo Ag Housing of an electric motor
US7591147B2 (en) 2006-11-01 2009-09-22 Honeywell International Inc. Electric motor cooling jacket resistor
JP4967510B2 (en) 2006-08-03 2012-07-04 パナソニック株式会社 refrigerator
DE102007009394A1 (en) 2007-02-21 2008-08-28 Alfred Kärcher Gmbh & Co. Kg Motor pump unit
JP5131103B2 (en) 2008-09-11 2013-01-30 スズキ株式会社 Motorcycle handle switch

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ES2461840T3 (en) 2014-05-21
US20120034112A1 (en) 2012-02-09
AU2009339813A1 (en) 2011-09-01
US8734129B2 (en) 2014-05-27
WO2010091699A1 (en) 2010-08-19
DK2396550T3 (en) 2014-05-26
EP2396550A1 (en) 2011-12-21
CN102292550A (en) 2011-12-21
AU2009339813B2 (en) 2014-04-03
PL2396550T3 (en) 2014-09-30

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