EP0027077B1 - Compact pump driven by an electric motor - Google Patents

Compact pump driven by an electric motor Download PDF

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Publication number
EP0027077B1
EP0027077B1 EP80401383A EP80401383A EP0027077B1 EP 0027077 B1 EP0027077 B1 EP 0027077B1 EP 80401383 A EP80401383 A EP 80401383A EP 80401383 A EP80401383 A EP 80401383A EP 0027077 B1 EP0027077 B1 EP 0027077B1
Authority
EP
European Patent Office
Prior art keywords
motor
chamber
seal
housing
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP80401383A
Other languages
German (de)
French (fr)
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EP0027077A1 (en
Inventor
Pierre Pressaco
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.)
CESSIONE;SOCIETE DES CABLES DU MANS S.A.
Original Assignee
DBA SA
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Filing date
Publication date
Application filed by DBA SA filed Critical DBA SA
Publication of EP0027077A1 publication Critical patent/EP0027077A1/en
Application granted granted Critical
Publication of EP0027077B1 publication Critical patent/EP0027077B1/en
Expired 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/086—Sealings especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/602—Drainage
    • F05D2260/6022—Drainage of leakage having past a seal

Definitions

  • the invention relates to a device forming a pump actuated by an electric motor, of a very compact design requiring in particular a new type of seal placed between the hydraulic circuit of the pump and said electric motor, and more particularly a device forming an automatic pump. for windshield washer used in a motor vehicle.
  • the invention relates more specifically to a device forming a pump actuated by an electric motor, of the type comprising a first chamber having a liquid inlet and a liquid outlet, a discharge means, such as an impeller or the like, being provided for forcing said liquid from said inlet to said outlet, and a second chamber encapsulating an electric motor, the delivery means being mechanically coupled to the shaft of the electric motor, said first and second chambers being adjacent and essentially separated by a seal made of material elastically compressible, comprising a static sealing portion, substantially peripheral, and a dynamic sealing portion, substantially central, defining a shaft passage through which said shaft of said motor passes, the first chamber being defined by a first housing part and the second chamber being defined at least partially by a second housing part comprising s means for receiving the engine, the two housing parts being mutually assembled to form the device.
  • a device of this kind is described in document DE-A-2 748 165.
  • the seal separating the pump chamber from the motor housing is slightly compressed during assembly, that is to say at time of assembly of the shells, to allow it to play a static sealing role; however, the mounting of these shells is unreliable insofar as the axial locking of the motor is achieved by positive stops (constituted by shoulders of the housing) carried respectively by the shells.
  • the assembly is therefore as follows: we introduce the motor inside one of the shells with the seal and the rotor in place on the axis of the engine and we close the housing by slightly compressing the seal (to make it play its sealing role) until the two axial faces of the motor come into contact with the shoulders.
  • the shells are permanently secured at the level of their overlapping parts by bonding or welding.
  • the need to keep the two shells in contact with the two axial ends of the motor throughout the assembly of the shells by gluing or welding is disadvantageous for a farbrication chain in large series.
  • Gluing or welding is in itself a time-consuming method of assembly, but it is the only one which can in fact be reasonably used in connection with the two-shoulder system, since a rapid assembly arrangement, as for example means cooperating by embedding, cannot guarantee (given the molding tolerances of the shells) both a secure immobilization of the engine and a sufficient compression of the seal allowing it to play its role of static sealing.
  • the invention makes it possible to solve the drawbacks of devices with two shells of the type defined above and in particular to use snap-shaped connections for assembling the shells by means of a new type of seal.
  • the device forming a pump actuated by an electric motor of the type defined above is characterized in that the two housing parts are mutually assembled by form of snap connections, and in that that a spring means is inserted and placed under compression, during assembly, between the seal and the motor and constitutes the pump side the only means for immobilizing the motor inside the second chamber between an end zone axial thereof and the spring means.
  • the device represented in FIG. 1 comprises a plastic casing constituted by the fitting of two parts 11 and 12.
  • the casing part 11 is shaped to define a first chamber 13 provided with a liquid inlet 14, upper, and a liquid outlet 15, lower.
  • the housing part 12 defines the essentials of a second chamber 16 housing an electric motor 17, the shaft 18 protrudes inside the first chamber 13 through a seal 19 of compressible material.
  • a discharge means constituted in the example described by an impeller 20, or the like, is mounted on the shaft 18. This impeller therefore defines with the first chamber 13 a kind of centrifugal pump since, when it is driven in rotation by the motor 17, liquid is sucked in from the inlet 14 and discharged towards the outlet 15 situated substantially in the radial extension of the said impeller 20.
  • a flexible conduit (not shown) is connected to the outlet 15 and connected to a use circuit leading for example to the ejection nozzles directed towards the windshield and possibly the rear window of a vehicle, if the device is used in a windshield washer installation, in accordance with the purpose immediately aimed at the invention.
  • the inlet 14 is engaged in the bottom wall of a liquid tank 21, partially shown in Figure 1, so that the centrifugal pump described above is naturally primed permanently as long as the tank 21 contains enough liquid.
  • the housing part 11 has an annular shoulder 25 which marks the limit of the first chamber 13.
  • the seal 19 bears against this shoulder by means of a thrust washer 26.
  • the housing part 11 extends beyond the 'shoulder 25 by a tubular portion 27, which defines a part of the second chamber 16 and whose outer diameter corresponds to the inner diameter of the housing portion 12, in which the portion 27 is engaged and locked by the snap-fit connections 28, allowing instant mounting.
  • the motor 17 has a generally cylindrical shape and the internal diameter of the portion 27 corresponds to the external diameter of the motor 17 so that the portion 27 plays, at least approximately, the role of centering member for the motor 17
  • Centering ribs 29 are also provided inside the housing part 12, just as a boss 30 or the like projecting relative to the bottom wall of the motor 17 is engaged in a corresponding cavity 31 of the housing part 12 to ensure, as far as possible, a relatively precise positioning of the motor inside the device.
  • the seal 19 is completely molded in an elastically compressible material, such as rubber. It is housed inside the portion 27 and bears against the shoulder 25, so that said first and second chambers are adjacent and essentially separated by the seal 19.
  • This seal (apart from a certain number of protrusions 32 protruding inside the second chamber 16 and whose function will be analyzed in detail below) has the general shape of a relatively thick disc whose outside diameter corresponds substantially to the inside diameter of the portion 27. The whole of the however, the gasket is slightly compressed when mounted both radially and in thickness.
  • a static sealing portion 35 substantially peripheral, and a dynamic sealing portion 36, substantially central intended to ensure sealing at the level of the shaft 18 and therefore shaped to define a shaft passage 37 normally crossed by the shaft 18 of the motor 17.
  • the center line 18a symbolizes the position of the shaft 18, when the seal 19 is in position in the portion 27.
  • the static sealing portion 35 we see that it comprises two external peripheral beads 38, 39, continuous, extending radially outward relative to the axis 18a and spaced parallel one of the another in a direction parallel to this axis.
  • the cylindrical lateral surface 40 of the seal which is between these two beads has a diameter corresponding substantially to the internal diameter of the portion 27, so that the beads 38 and 39 will necessarily be compressed during assembly to guarantee a certain seal.
  • a continuous peripheral groove 41 is formed in said static sealing portion 35, in the vicinity of the bead 38. This improves the flexibility of the compressible material in the vicinity of the bead 38.
  • the static sealing portion 35 comprises also a continuous bead 42 extending parallel to the direction of the axis 18a and directed towards the first chamber 13, when the seal is in its mounting position. In this way, after mounting, this bead 42 will be deformed in compression against the thrust washer 26, itself in abutment on the shoulder 25.
  • the dynamic sealing portion 36 is shaped so as to have two continuous internal peripheral flanges 45, 46, extending radially inward of the shaft passage 37. These internal flanges are spaced parallel to the one of the other in a direction parallel to the axis 18a. These two beads 45 and 46 therefore define two annular throttles centered on the axis 18a and of the same diameter. Of course, the diameter of these two throttles is less than the diameter of the shaft 18, to ensure a suitable seal at the latter. It is especially advantageous to provide two contact zones spaced from one another along the shaft 18, between the latter and the seal 19, as is the case thanks to the two beads 45 and 46.
  • the intermediate portion of the seal located between said static and dynamic sealing portions includes in particular a decoupling groove 50, extending relatively deep in the thickness of the seal 19, to give more flexibility to this middle portion and avoid, as much as it may be possible that the deformations necessary for assembly; in one of the sealing portions does not cause harmful stresses in the other portion, likely to affect the sealing efficiency.
  • the circular groove 48 can also be considered as a decoupling groove, given its relatively large depth.
  • the protrusions 32 protruding after mounting in the second chamber 16 came integrally with the seal 19 and distributed substantially in circular symmetry all around the axis 18a. Their length is sufficient to come crashing partially against the motor frame 17 at the time of assembly of the housing parts 11 and 12. All of these protrusions therefore form a sort of spring interposed and mounted in compression between the rest of the seal 19 and the motor 17, to immobilize the latter inside the second chamber 16.
  • a protective disc 51 is fixed on the shaft 18 so as to rotate with it in the second chamber 16, between the seal 19 and the motor 17. Furthermore, a liquid discharge orifice 52 is formed in the side wall of this second chamber, this orifice preferably being located at the lower part of the housing considering the normal mounting position illustrated in FIG. 1 and substantially in the radial extension of the protective disc 51.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

L'invention se rapporte à un dispositif formant pompe à actionnement par moteur électrique, d'une conception très compacte nécessitant notamment un nouveau type de joint placé entre le circuit hydraulique de la pompe et ledit moteur électrique, et plus particulièrement un dispositif formant pompe automatique pour lave-glace utilisable dans un véhicule automobile.The invention relates to a device forming a pump actuated by an electric motor, of a very compact design requiring in particular a new type of seal placed between the hydraulic circuit of the pump and said electric motor, and more particularly a device forming an automatic pump. for windshield washer used in a motor vehicle.

L'invention concerne plus spécifiquement un dispositif formant pompe à actionnement par moteur électrique, du type comportant une première chambre ayant une entrée de liquide et une sortie de liquide, un moyen de refoulement, tel qu'une roue à aubes ou analogue, étant prévu pour forcer ledit liquide depuis ladite entrée vers ladite sortie, et une seconde chambre encapsulant un moteur électrique, le moyen de refoulement étant mécaniquement couplé à l'arbre du moteur électrique, lesdites première et seconde chambres étant adjacentes et essentiellement séparées par un joint en matériau élastiquement compressible, comportant une portion d'étanchement statique, sensiblement périphérique, et une portion d'étanchement dynamique, sensiblement centrale, définissant un passage d'arbre traversé par ledit arbre dudit moteur, la première chambre étant définie par une premiere partie de boitier et la seconde chambre étant définie au moins partiellement par une seconde partie de boîtier comprenant des moyens de réception du moteur, les deux parties de boîtier étant mutuellement assemblées pour la constituion du dispositif.The invention relates more specifically to a device forming a pump actuated by an electric motor, of the type comprising a first chamber having a liquid inlet and a liquid outlet, a discharge means, such as an impeller or the like, being provided for forcing said liquid from said inlet to said outlet, and a second chamber encapsulating an electric motor, the delivery means being mechanically coupled to the shaft of the electric motor, said first and second chambers being adjacent and essentially separated by a seal made of material elastically compressible, comprising a static sealing portion, substantially peripheral, and a dynamic sealing portion, substantially central, defining a shaft passage through which said shaft of said motor passes, the first chamber being defined by a first housing part and the second chamber being defined at least partially by a second housing part comprising s means for receiving the engine, the two housing parts being mutually assembled to form the device.

Un dispositif de ce genre est décrit dans le document DE-A-2 748 165. Dans ce document, le joint d'étanchéité séparant la chambre de la pompe du logement du moteur est légèrement comprimé au montage c'est-à-dire au moment de l'assemblage des coquilles, pour lui permettre de jouer un rôle d'étanchement statique; cependant, le montage de ces coquilles se fait de façon peu fiable dans la mesure où le blocage axial du moteur est réalisé par des butées positives (constituées par des épaulements du boîtier) portées respectivement par les coquilles. Le montage est donc le suivant: on introduit le moteur à l'intérieur de l'une des coquilles avec le joint et le rotor en place sur l'axe du moteur et on referme le boîtier en comprimant légèrement le joint (pour lui faire jouer son rôle d'étanchéité) jusqu'à ce que les deux faces axiales du moteur entrent en contact avec les épaulements. Puis, en maintenant l'assemblage dans cette position, on solidarise définitivement les coquilles au niveau de leurs parties en recouvrement par collage ou soudure. Dans ce document, il est également envisagé, en variante, d'assembler les coquilles par une liaison à baïonnette. La nécessité de maintenir les deux coquilles en contact avec les deux extrémités axiales du moteur pendant toute la durée de l'assemblage des coquilles par collage ou soudure est désavantageuse pour une chaîne de farbrication en grande série. Le collage ou la soudure est en soi un mode d'assemblage qui fait perdre beaucoup de temps, mais c'est le seul qui puisse en fait être raisonnablement utilisé en liaison avec le système à deux épaulements, car un agencement d'assemblage rapide, comme par exemple des moyens coopérant par encastrement, ne peut garantir (étant données les tolérances de moulage des coquilles) à la fois une immobilisation sûre du moteur et une compression suffisante du joint lui permettant de jouer son rôle d'étanchéité statique.A device of this kind is described in document DE-A-2 748 165. In this document, the seal separating the pump chamber from the motor housing is slightly compressed during assembly, that is to say at time of assembly of the shells, to allow it to play a static sealing role; however, the mounting of these shells is unreliable insofar as the axial locking of the motor is achieved by positive stops (constituted by shoulders of the housing) carried respectively by the shells. The assembly is therefore as follows: we introduce the motor inside one of the shells with the seal and the rotor in place on the axis of the engine and we close the housing by slightly compressing the seal (to make it play its sealing role) until the two axial faces of the motor come into contact with the shoulders. Then, by maintaining the assembly in this position, the shells are permanently secured at the level of their overlapping parts by bonding or welding. In this document, it is also envisaged, as a variant, to assemble the shells by a bayonet connection. The need to keep the two shells in contact with the two axial ends of the motor throughout the assembly of the shells by gluing or welding is disadvantageous for a farbrication chain in large series. Gluing or welding is in itself a time-consuming method of assembly, but it is the only one which can in fact be reasonably used in connection with the two-shoulder system, since a rapid assembly arrangement, as for example means cooperating by embedding, cannot guarantee (given the molding tolerances of the shells) both a secure immobilization of the engine and a sufficient compression of the seal allowing it to play its role of static sealing.

Le document US-A-3 576 380 décrit par ailleurs suivant une approche différente, un dispositif formant pompe comportant un bloc moteur, avec un moteur électrique noyé dans un boîtier fermé, rapporté sur un boîtier de pompe et fixé à ce dernier par rivetage.Document US-A-3,576,380 also describes, using a different approach, a pump device comprising a motor unit, with an electric motor embedded in a closed housing, attached to a pump housing and fixed to the latter by riveting.

L'invention permet de résoudre les inconvénients des dispositifs à deux coquilles du type défini plus haut et notamment d'utiliser des liaisons de forme à encliquetage pour l'assemblage des coquilles grâce à un nouveau type de joint d'étanchéité.The invention makes it possible to solve the drawbacks of devices with two shells of the type defined above and in particular to use snap-shaped connections for assembling the shells by means of a new type of seal.

Pour ce faire, selon une caractéristique de l'invention, le dispositif formant pompe à actionnement par moteur électrique du type défini plus haut est caractérisé en ce que les deux parties de boîtier sont mutuellement assemblées par des liaisons de forme à encliquetage, et en ce qu'un moyen formant ressort est intercalé et mis en compression , lors de l'assemblage, entre le joint et le moteur et constitue côté pompe le seul moyen pour immobiliser le moteur à l'intérieur de la seconde chambre entre une zone d'extrémité axiale de celle-ci et le moyen formant ressort.To do this, according to a characteristic of the invention, the device forming a pump actuated by an electric motor of the type defined above is characterized in that the two housing parts are mutually assembled by form of snap connections, and in that that a spring means is inserted and placed under compression, during assembly, between the seal and the motor and constitutes the pump side the only means for immobilizing the motor inside the second chamber between an end zone axial thereof and the spring means.

L'invention sera mieux comprise et d'autres détails et avantages de celle-ci apparaîtront mieux à la lumière de la description détaillée qui va suivre d'un dispositif formant pompe selon l'invention, donnée uniquement à titre d'exemple et faite en référence aux dessins non limitatifs annexés dans lesquels:

  • - la figure 1 est une vue en coupe du dispositif conforme à l'invention; et
  • - la figure 2 est une vue en coupe et à plus grande échelle d'un joint en matériau compressible utilisé dans le dispositif de la figure 1.
The invention will be better understood and other details and advantages thereof will appear better in the light of the detailed description which follows of a device forming a pump according to the invention, given solely by way of example and made in reference to the nonlimiting drawings annexed in which:
  • - Figure 1 is a sectional view of the device according to the invention; and
  • - Figure 2 is a sectional view on a larger scale of a seal of compressible material used in the device of Figure 1.

Le dispositif représenté sur la figure 1 comporte un boîtier en matière plastique constitué par l'emboîtage de deux parties 11 et 12. La partie de boîtier 11 est conformée pour définir une première chambre 13 munie d'une entrée de liquide 14, supérieure, et d'une sortie de liquide 15, inférieure. La partie de boîtier 12 définit l'essentiel d'une seconde chambre 16 abritant un moteur électrique 17 dont l'arbre 18 fait saiilie à l'intérieure de la première chambre 13 en traversant un joint 19 en matériau compressible. Un moyen de refoulement constitué dans l'exemple décrit par une roue à aubes 20, ou analogue, est monté sur l'arbre 18. Cette roue à aubes définit donc avec la première chambre 13 une sorte de pompe centrifuge puisque, lorsqu'elle est entraînée en rotation par le moteur 17, du liquide est aspiré depuis l'entrée 14 et refoulé vers la sortie 15 située sensiblement dans le prolongement radial de ladite roue à aubes 20. Un conduit souple (non représenté) est raccordé à la sortie 15 et relié à un circuit d'utilisation aboutissant par exemple aux embouts d'éjection dirigés vers le pare-brise et éventuellement la vitre arrière d'un véhicule, si le dispositif est utilisé dans une installation de lave-glace, conformément au but immédiatement visé par l'invention. Par ailleurs, l'entrée 14 est engagée dans la paroi de fond d'un réservoir de liquide 21, représenté partiellement sur la Figure 1, de sorte que la pompe centrifuge décrite ci-dessus soit naturellement amorcée en permanence tant que le réservoir 21 contient suffisamment de liquide. La partie de boîtier 11 comporte un épaulement annulaire 25 qui marque la limite de la première chambre 13. Le joint 19 prend appui contre cet épaulement par l'intermédiaire d'une rondelle de butée 26. La partie de boîtier 11 se prolonge audelà de l'épaulement 25 par une portion tubulaire 27, qui définit une partie de la seconde chambre 16 et dont le diamètre extérieur correspond au diamètre intérieur de la partie de boîtier 12, dans laquelle la portion 27 est engagée et verrouillée par les liaisons de forme à encliquetage 28, permettant un montage instantané. De façon classique, le moteur 17 a une forme générale cylindrique et le diamètre intérieur de la portion 27 correspond au diamètre extérieur du moteur 17 de sorte que la portion 27 joue, au moins approximativement, le rôle d'organe de centrage pour le moteur 17. Des nervures de centrage 29 sont également prévues à l'intérieur de la partie de boîtier 12, de même qu'un bossage 30 ou analogue faisant saillie par rapport à la paroi de fond du moteur 17 est engagé dans une cavité 31 correspondante de la partie de boîtier 12 pour assurer, autant que faire se peut, un positionnement relativement précis du moteur à l'intérieur du dispositif. On va maintenant décrire la structure du joint 19, en référence à la figure 2. Le joint 19 est entièrement moulé dans un matériau élastiquement compressible, tel que du caoutchouc. Il est logé à l'intérieur de la portion 27 et prend appui contre l'épaulement 25, de sorte que lesdites première et seconde chambres sont adjacentes et essentiellement séparées par le joint 19. Ce joint (mis à part un certain nombre de protubérances 32 faisant saillie à l'intérieur de la seconde chambre 16 et dont la fonction sera analysée en détail plus loin) a la forme générale d'un disque relativement épais dont le diamètre extérieur correspond sensiblement au diamètre intérieur de la portion 27. L'ensemble du joint est cependant légèrement comprimé au montage tant radialement qu'en épaisseur. Il se compose essentiellement d'une portion d'étanchement statique 35, sensiblement périphérique, et d'une portion d'étanchement dynamique 36, sensiblement centrale destinée à assurer l'étanchéité au niveau de l'arbre 18 et conformée de ce fait pour définir un passage d'arbre 37 normalement traversé par l'arbre 18 du moteur 17. Sur la figure 2, le trait d'axe 18a symbolise la position de l'arbre 18, lorsque le joint 19 est en position dans la portion 27. Si on considère la portion d'étanchement statique 35, on constate qu'elle comporte deux bourrelets périphériques externes 38, 39, continus, s'étendant radialement vers l'extérieur par rapport à l'axe 18a et espacés parallèlement l'un de l'autre suivant une direction parallèle à cet axe. Bien entendu, la surface latérale cylindrique 40 du joint qui est comprise entre ces deux bourrelets a un diamètre correspondans sensiblement au diamètre interne de la portion 27, de sorte que les bourrelets 38 et 39 seront nécessairement comprimés au montage pour garantir une certaine étanchéité. On remarquera également qu'une gorge périphérique 41, continue, est pratiquée dans ladite portion d'étanchement statique 35, au voisinage du bourrelet 38. Ceci améliore la flexibilité du matériau compressible au voisinage du bourrelet 38. La portion d'etanchement statique 35 comporte également un bourrelet continu 42 s'étendant parallèlement à la direction de l'axe 18a et dirigé vers la première chambre 13, lorsque le joint est dans sa position de montage. De cette façon, après montage, ce bourrelet 42 sera déformé en compression contre la rondelle de butée 26, elle-même en appui sur l'épaulement 25.The device represented in FIG. 1 comprises a plastic casing constituted by the fitting of two parts 11 and 12. The casing part 11 is shaped to define a first chamber 13 provided with a liquid inlet 14, upper, and a liquid outlet 15, lower. The housing part 12 defines the essentials of a second chamber 16 housing an electric motor 17, the shaft 18 protrudes inside the first chamber 13 through a seal 19 of compressible material. A discharge means constituted in the example described by an impeller 20, or the like, is mounted on the shaft 18. This impeller therefore defines with the first chamber 13 a kind of centrifugal pump since, when it is driven in rotation by the motor 17, liquid is sucked in from the inlet 14 and discharged towards the outlet 15 situated substantially in the radial extension of the said impeller 20. A flexible conduit (not shown) is connected to the outlet 15 and connected to a use circuit leading for example to the ejection nozzles directed towards the windshield and possibly the rear window of a vehicle, if the device is used in a windshield washer installation, in accordance with the purpose immediately aimed at the invention. Furthermore, the inlet 14 is engaged in the bottom wall of a liquid tank 21, partially shown in Figure 1, so that the centrifugal pump described above is naturally primed permanently as long as the tank 21 contains enough liquid. The housing part 11 has an annular shoulder 25 which marks the limit of the first chamber 13. The seal 19 bears against this shoulder by means of a thrust washer 26. The housing part 11 extends beyond the 'shoulder 25 by a tubular portion 27, which defines a part of the second chamber 16 and whose outer diameter corresponds to the inner diameter of the housing portion 12, in which the portion 27 is engaged and locked by the snap-fit connections 28, allowing instant mounting. Conventionally, the motor 17 has a generally cylindrical shape and the internal diameter of the portion 27 corresponds to the external diameter of the motor 17 so that the portion 27 plays, at least approximately, the role of centering member for the motor 17 Centering ribs 29 are also provided inside the housing part 12, just as a boss 30 or the like projecting relative to the bottom wall of the motor 17 is engaged in a corresponding cavity 31 of the housing part 12 to ensure, as far as possible, a relatively precise positioning of the motor inside the device. We will now describe the structure of the seal 19, with reference to Figure 2. The seal 19 is completely molded in an elastically compressible material, such as rubber. It is housed inside the portion 27 and bears against the shoulder 25, so that said first and second chambers are adjacent and essentially separated by the seal 19. This seal (apart from a certain number of protrusions 32 protruding inside the second chamber 16 and whose function will be analyzed in detail below) has the general shape of a relatively thick disc whose outside diameter corresponds substantially to the inside diameter of the portion 27. The whole of the however, the gasket is slightly compressed when mounted both radially and in thickness. It essentially consists of a static sealing portion 35, substantially peripheral, and a dynamic sealing portion 36, substantially central intended to ensure sealing at the level of the shaft 18 and therefore shaped to define a shaft passage 37 normally crossed by the shaft 18 of the motor 17. In FIG. 2, the center line 18a symbolizes the position of the shaft 18, when the seal 19 is in position in the portion 27. If we consider the static sealing portion 35, we see that it comprises two external peripheral beads 38, 39, continuous, extending radially outward relative to the axis 18a and spaced parallel one of the another in a direction parallel to this axis. Of course, the cylindrical lateral surface 40 of the seal which is between these two beads has a diameter corresponding substantially to the internal diameter of the portion 27, so that the beads 38 and 39 will necessarily be compressed during assembly to guarantee a certain seal. It will also be noted that a continuous peripheral groove 41 is formed in said static sealing portion 35, in the vicinity of the bead 38. This improves the flexibility of the compressible material in the vicinity of the bead 38. The static sealing portion 35 comprises also a continuous bead 42 extending parallel to the direction of the axis 18a and directed towards the first chamber 13, when the seal is in its mounting position. In this way, after mounting, this bead 42 will be deformed in compression against the thrust washer 26, itself in abutment on the shoulder 25.

De façon analogue, la portion d'étanchement dynamique 36 est conformée de façon à présenter deux bourrelets périphériques internes 45, 46, continus, s'étendant radialement vers l'intérieur du passage d'arbre 37. Ces bourrelets internes sont espacés parallèlement l'un de l'autre suivant une direction parallèle à l'axe 18a. Ces deux bourrelets 45 et 46 définissent donc deux étranglements annulaires centrés sur l'axe 18a et de même diamètre. Bien entendu, le diamètre de ces deux étranglements est inférieur au diamètre de l'arbre 18, pour assurer une étanchéité convenable au niveau de ce dernier. Il est spécialement avantageux de prévoir deux zones de contact espacées l'une de l'autre le long de l'arbre 18, entre ce dernier et le joint 19, comme cela est le cas grâce aux deux bourrelets 45 et 46. En effet, en cas de centrage imparfait du moteur 17 à l'intérieur du boîtier, après montage, un léger décalage entre la position réelle de l'arbre 18 et sa position souhaitée symbolisée par l'axe 18a, serait susceptible de provoquer de légères fuites le long de l'arbre 18. On a constaté que la présence des deux bourrelets 45 et 46 espacés axialement apportait une solution satisfaisante à ce problème. D'autre part, une gorge circulaire 48 continue est pratiquée dans ladite portion d'étanchement dynamique 36 au voisinage du bourrelet 45, pour donner plus de souplesse à ce dernier et permettre un meilleur contact permament entre ledit bourrelet 45 et l'arbre tournant 18. Pour la même raison; le bourrelet périphérique 46 est défini au voisinage de t'extrémité d'une lèvre annulaire 49, sensiblement tronconique.Similarly, the dynamic sealing portion 36 is shaped so as to have two continuous internal peripheral flanges 45, 46, extending radially inward of the shaft passage 37. These internal flanges are spaced parallel to the one of the other in a direction parallel to the axis 18a. These two beads 45 and 46 therefore define two annular throttles centered on the axis 18a and of the same diameter. Of course, the diameter of these two throttles is less than the diameter of the shaft 18, to ensure a suitable seal at the latter. It is especially advantageous to provide two contact zones spaced from one another along the shaft 18, between the latter and the seal 19, as is the case thanks to the two beads 45 and 46. Indeed, in the event of imperfect centering of the motor 17 inside the housing, after assembly, a slight offset between the real position of the shaft 18 and its desired position symbolized by the axis 18a, would be liable to cause slight leaks along of the shaft 18. It has been found that the presence of the two beads 45 and 46 spaced axially provided a satisfactory solution to this problem. On the other hand, a continuous circular groove 48 is practiced in said dynamic sealing portion 36 in the vicinity of the bead 45, to give more flexibility to the latter and allow better permanent contact between said bead 45 and the rotating shaft 18. For the same reason; the peripheral bead 46 is defined in the vicinity of the end of an annular lip 49, substantially frustoconical.

La partie intermédiaire du joint située entre lesdites portions d'étanchement statique et dynamique comporte notamment une gorge de découplage 50, s'étendant relativement profondément dans l'épaisseur du joint 19, pour donner plus de souplesse à cette partie médiane et éviter, autant que faire se peut, que les déformations, nécessaires au montage; dans l'une des portions d'étanchement n'engendrent des contraintes nuisibles dans l'autre portion, susceptibles d'en affecter l'efficacité d'étanchement. Il est à noter que dans le mode de réalisation décrit à la figure 2, la gorge circulaire 48 peut être aussi considérée comme une gorge de découplage, étant donné sa profondeur relativement importante.The intermediate portion of the seal located between said static and dynamic sealing portions includes in particular a decoupling groove 50, extending relatively deep in the thickness of the seal 19, to give more flexibility to this middle portion and avoid, as much as it may be possible that the deformations necessary for assembly; in one of the sealing portions does not cause harmful stresses in the other portion, likely to affect the sealing efficiency. It should be noted that in the embodiment described in FIG. 2, the circular groove 48 can also be considered as a decoupling groove, given its relatively large depth.

Comme mentionné précédemment, les protubérances 32 faisant saillie, après montage, dans la seconde chambre 16 sont venues de matière avec le joint 19 et réparties sensiblement en symétrie circulaire tout autour de l'axe 18a. Leur longueur est suffisante pour venir s'écraser partiellement contre le bâti du moteur 17 au moment de l'assemblage des parties de boîtier 11 et 12. L'ensemble de ces protubérances forme donc une sorte de ressort intercalé et monté en compression entre le reste du joint 19 et le moteur 17, pour immobiliser ce dernier à l'intérieur de la seconde chambre 16.As mentioned previously, the protrusions 32 protruding after mounting in the second chamber 16 came integrally with the seal 19 and distributed substantially in circular symmetry all around the axis 18a. Their length is sufficient to come crashing partially against the motor frame 17 at the time of assembly of the housing parts 11 and 12. All of these protrusions therefore form a sort of spring interposed and mounted in compression between the rest of the seal 19 and the motor 17, to immobilize the latter inside the second chamber 16.

En se reportant de nouveau à la figure 1, on remarquera qu'un disque de protection 51 est fixé sur l'arbre 18 de façon à tourner avec lui dans la seconde chambre 16, entre le joint 19 et le moteur 17. En outre, un orifice d'évacuation de liquide 52 est ménagé dans la paroi latérale de cette seconde chambre, cet orifice étant de préférence situé à la partie inférieure du boîtier en considérant la position normale de montage illustrée sur la figure 1 et sensiblement dans le prolongement radial du disque de protection 51. Ainsi, en cas de légère défaillance de la portion d'étanchement dynamique 36, si du liquide parvient à pénétrer dans la seconde chambre 16 en s'écoulant le long de l'arbre 18, il est immédiatement dévié vers la paroi latérale de la portion 27 et finit par être évacué grâce à l'orifice 52, le rotor et les bobinages du moteur 17 étant ainsi protégés de l'humidité.Referring again to FIG. 1, it will be noted that a protective disc 51 is fixed on the shaft 18 so as to rotate with it in the second chamber 16, between the seal 19 and the motor 17. Furthermore, a liquid discharge orifice 52 is formed in the side wall of this second chamber, this orifice preferably being located at the lower part of the housing considering the normal mounting position illustrated in FIG. 1 and substantially in the radial extension of the protective disc 51. Thus, in the event of slight failure of the dynamic sealing portion 36, if liquid manages to penetrate the second chamber 16 by flowing along the shaft 18, it is immediately deflected towards the side wall of the portion 27 and ends up being evacuated through the orifice 52, the rotor and the windings of the motor 17 thus being protected from humidity.

Bien entendu, l'invention n'est nullement limitée au mode de réalisation du dispositif qui vient d'être décrit.Of course, the invention is in no way limited to the embodiment of the device which has just been described.

Claims (4)

1. A compact pump driven by an electric motor, comprising a first chamber (13) having liquid inlet means (14) and liquid outlet means (15), feed means, e. g. an impeller (20) or the like adapted to force said liquid from said inlet means towards said outlet means, and a second chamber (16) encapsulating an electric motor (17), said feed means being mechanically coupled to the shaft (18) of said electric motor, said first and second chambers being adjacent to one another and being essentially separated by seal means (19) made from elastically compressible material, said seal means having a static seal portion (35) extending essentially in peripheral direction as weir as an essentially central dynamic seal portion (36) defining a shaft opening (37), said shaft of said motor extending therethrough, the first chamber (13) being defined by a first part (11) of said housing and the second chamber (16) being at least parially defined by a second part (12) of said housing being formed with motor receiving means (29. 31), said two parts of the housing being mutually assembled to form said compact pump, charac. terized in that the two parts (11, 12) of the housing are mutually assembled by means of snap connections (28) and in that spring means (32) are interposed between said seal means (19) and said motor (17) being compressed upon assembly of the pump, said spring means forming the only pumpside fixing means of the motor to position the latter in the interior of the second chamber (16) between an axial end zone (31) of said chamber and said spring means.
2. A compact pump as in claim 1, characterized in that said spring means is formed by a plurality of axial projections (32) made from compressible. material and being distributed around said shaft (18) in a pattern of essentially circular symmetry.
3. The compact pump as in claim 2, characterized in that said seal means and said spring means are combined, said projections (32) being formed integral with the seal means and projecting therefrom in the direction of the motor (17).
4: The compact pump as in one of claims 1 to 3, characterized in that the first part (11) of the housing comprises a projecting tubular portion (27) defining part of the second chamber (16) and defining reception means for said motor (17).
EP80401383A 1979-10-04 1980-09-30 Compact pump driven by an electric motor Expired EP0027077B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7924711 1979-10-04
FR7924711A FR2466644A1 (en) 1979-10-04 1979-10-04 ELECTRIC MOTOR-POWERED COMPACT PUMP IMPROVEMENTS TO PROGRAM SELECTING DEVICES FOR RADIO-ELECTRIC RECEIVERS

Publications (2)

Publication Number Publication Date
EP0027077A1 EP0027077A1 (en) 1981-04-15
EP0027077B1 true EP0027077B1 (en) 1984-02-01

Family

ID=9230304

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Application Number Title Priority Date Filing Date
EP80401383A Expired EP0027077B1 (en) 1979-10-04 1980-09-30 Compact pump driven by an electric motor

Country Status (5)

Country Link
EP (1) EP0027077B1 (en)
JP (1) JPS5656995A (en)
DE (1) DE3066415D1 (en)
ES (1) ES495619A0 (en)
FR (1) FR2466644A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2520844A1 (en) * 1982-02-03 1983-08-05 Chausson Usines Sa SUPPORT FOR MISCELLANEOUS MECHANISMS OF MOTOR-VENTILATORS, COMPRESSORS, PUMPS AND THE LIKE
GB8427606D0 (en) * 1983-11-17 1984-12-05 Bosch Siemens Hausgeraete Pump unit
IT1218569B (en) * 1987-04-22 1990-04-19 Askoll Srl CENTRIFIGE PUMP PERFECT FOR WASHING MACHINES, DISHWASHER AND APPLIANCES IN GENERAL
ES2020756A6 (en) * 1990-02-05 1991-09-16 Transpar Iberica Sa Impeller pump of cleaning liquid for motor vehicles.
FR2658567A1 (en) * 1990-02-16 1991-08-23 Electro Mec Nivernais CENTRIFUGAL MOTOR PUMP.
US5833441A (en) * 1996-06-19 1998-11-10 Itt Automotive Electrical Systems, Inc. Windshield wiper washer motor for use in a vehicle

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1728415A1 (en) * 1965-11-19 1972-08-10 Beteiligungs Ag Haustechnik Induction motor pump
US3370608A (en) * 1966-08-12 1968-02-27 Whirlpool Co Liquid handling apparatus with pump means having mount and seal
US3408942A (en) * 1967-05-23 1968-11-05 Crowell Designs Inc Bilge pump
US3576380A (en) * 1969-08-11 1971-04-27 Mccord Corp Motor and pump assembly
DE2748165A1 (en) * 1977-10-27 1979-05-03 Helphos Autolicht Schardmuelle Compact pump for windscreen washer - has two part plastics housing for integral motor clipped together by snap fasteners

Also Published As

Publication number Publication date
EP0027077A1 (en) 1981-04-15
ES8106042A1 (en) 1981-07-01
FR2466644A1 (en) 1981-04-10
DE3066415D1 (en) 1984-03-08
ES495619A0 (en) 1981-07-01
JPS5656995A (en) 1981-05-19
FR2466644B1 (en) 1983-12-23

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