FR2466644A1 - ELECTRIC MOTOR-POWERED COMPACT PUMP IMPROVEMENTS TO PROGRAM SELECTING DEVICES FOR RADIO-ELECTRIC RECEIVERS - Google Patents

Abstract

THIS IS A SWITCH BLOCK ALLOWING TO SELECT THE PROGRAMS RECEIVED BY A RECEIVER THROUGH THE ANGULAR MOVEMENTS OF M COMMAND BUTTONS ALIGNED 4, THE SWITCHES ALLOWING TO CONNECT AT WILL M PLOTS 1 TO ONE OR THE OTHER OF P CONDUCTOR RAILS 2. THIS BLOCK INCLUDES M COMBES 5, CONSTITUTED BY CUTTING AN ELASTIC METAL SHEET, OF WHICH THE BACKS 5 RECESSED IN THE BUILDING 6 OF THE BLOCK ARE CONNECTED TO THE PLOTS1 AND WHOSE TEETH 5 EXTEND PARALLEL TO THE TRACKS, BETWEEN THESE AND CAMS OF CONTROL 7 CARRIED BY BUTTONS DUE TO P CAMES PER BUTTON, OFFSET AXIALLY AND ANGULARLY BY 360P. PREFERRED APPLICATION: PROGRAM SELECTOR FOR TELEVISION RECEIVERS.

Description

The invention relates to a device forming a pump, actuating

  by electric motor, a very compact design requiring in particular a new type of seal placed between the circuit

  hydraulic pump and said electric motor.

  The invention is particularly concerned with

  industrial product, an automatic windshield washer pump,

sand in a motor vehicle.

  Several types of pumps operated by means of

  electric motor and especially intended to equip a washer system, in a motor vehicle. In particular, a device is known in which the pumping unit (for example of the pallet type) is immersed in the cleaning liquid reservoir and connected to the engine.

  electric actuator by a long shaft forming a transmission shaft

  the engine being mounted outside the tank, the

  more often on the cap of the latter. Such a system, although

  correctly, has certain inherent defects in its structure.

  In particular, it is bulky because the aforementioned pumping unit must be located as close as possible to the bottom of the tank to reduce the number of levelings of the latter, while the electric actuation motor must be located above of this tank. In addition, this structure uses a large number of parts assembled so that

  its cost price is relatively high.

  The invention aims to propose a new electric motor driven pump, which is both more compact and more construction. simple without its operating reliability being affected, in particular without there being any risk-leakage of liquid

  from the pumping unit to the actuating motor.

  In this spirit, the invention therefore relates to a device

  An electric motor driven pump, of the type having a first chamber having a liquid inlet and a liquid outlet and a delivery means, such as a paddle wheel or the like, forcing

  said liquid from said inlet to said outlet, as well as a

  room conde housing an electric motor; said discharge means being mechanically coupled to the shaft of said electric motor, characterized

  in that said first and second chambers are adjacent and substantially

  partially separated by a seal of elastically compressible material, comprising a substantially peripheral static sealing portion and a substantially central dynamic sealing portion defining

  a shaft passage traversed by said shaft of said motor.

  According to a preferred embodiment of the invention, said seal may be provided with a plurality of protuberances projecting inside said second chamber and acting as a spring mounted in compression between said sealing portions sta. - tick and dynamic said seal and said motor, to immobilize it

  inside said second chamber.

  The invention will be better understood and other details and

  advantages of it will appear better in the light of the description

  following detailed description of a device forming a pump according to the invention, given solely by way of example and with reference to the appended nonlimiting drawings in which

  - Figure 1 is a sectional view of the device con-

  form to the invention; and FIG. 2 is a view in section and on a larger scale of a compressible material seal used in the device of FIG.

Figure 1.

  The device shown in FIG. 1 comprises a plastic casing constituted by the casing of two parts 11 and 12. The casing part 11 is shaped to define a first chamber 13 provided with an upper liquid inlet 14, and a liquid outlet 15, lower. The housing portion 12 defines the essential 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 a bladed wheel 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 from the inlet 14 and discharged to the exit 15 si-

  substantially in the radial extension of said impeller 20.

  A flexible duct (not shown) is connected to the outlet 15 and connected to a utilization circuit terminating for example in the ejection tips directed towards the windshield and possibly the rear window of a

  vehicle, if the device is used in a washing installation

  ice, in accordance with the purpose immediately referred to by the invention. Moreover, the inlet 14 is engaged in the bottom wall of a liquid reservoir 21, partially shown in FIG. 1, so that the centrifugal pump described above is naturally permanently primed as long as the reservoir 21 contains enough liquid. The housing portion 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.

  housing 11 extends beyond the shoulder 25 by a tubular portion

  27, which defines a portion of the second chamber 16 and whose outer diameter corresponds to the inside diameter of the housing portion 12, in which the portion 27 is engaged and locked by cooperating embedding means 28. In a conventional manner, the motor 17 has a generally cylindrical shape and the inside diameter of the portion 27 corresponds to the outside diameter of the motor 17 so that the portion 27 plays, at least approximately, the role of centering member for

  the engine 17. Centering ribs 29 are also provided in the invention.

  the interior of the housing portion 12, as well as a boss 30 or the like protruding from the bottom wall of the motor 17 is engaged in a corresponding cavity 31 of the housing portion 12 to ensure as much as possible, a relatively precise positioning of the motor inside the device. We will now describe the structure of the

  joint 19, with reference to FIG.

  The seal 19 is entirely molded from an elastic material

  only compressible, such as rubber. It is housed inside

  of the portion 27 and bears against the shoulder 25, so that-

  say first and second rooms are adjacent and essentially

  separated by the joint 19. This joint (apart from a number of

  tubing 32 projecting inside the second chamber 16 and whose function will be analyzed in detail later) has the general shape of a relatively thick disc whose outer diameter substantially corresponds to the inner diameter of the portion 27. The However, the seal assembly is slightly compressed both radially and radially.

  thickness. It consists essentially of a portion of watertight

  static device 35, substantially peripheral, and a portion of

  36, substantially central for sealing at the shaft 18 and shaped thereby to define a shaft passage 37 normally traversed by the shaft 18 of the engine 17. In Figure 2, the line 18a axis symbolizes the position of the shaft 18, when

  the seal 19 is in position in the portion 27. If we consider the

  static sealing / it is found that it comprises two outer peripheral beads 38, 39, continuous, extending radially outwardly relative to the axis 18a and spaced parallel to each other in accordance with a direction parallel to this axis. Of course, the

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  cylindrical side surface 40 of the seal which is between these two beads has a diameter substantially corresponding to the internal diameter of the portion 27, so that the beads 38 and 39 will necessarily be compressed to the assembly to ensure a certain seal. It will also be noted that a peripheral groove 41, continuous, is made in said static sealing portion 35, in the vicinity of the bead 38.

  improves the flexibility of the compressible material, in the vicinity of the wadding

  38. The static sealing portion 35 also includes a filler

  Continuously 42 extends parallel to the direction of the axis 18a and is directed to the first chamber 13, when the seal is in its mounting position. In this way, after assembly, this bead 42 will be deformed in compression against the thrust washer 26, itself bearing on

the shoulder 25.

  Similarly, the dynamic sealing portion 36 is shaped so as to have two continuous peripheral inner bulges 46, extending radially inwardly of the shaft passage 37. These inner beads are spaced parallel to one another. the other in a direction parallel to the axis 18a. These two flanges and 46 thus define two annular constrictions - centered on the axis 18 and of the same diameter. Of course, the diameter of these two chokes is smaller than the diameter of the shaft 18, to ensure a

  proper sealing at the level of the latter. It is especially advantageous

  to provide two contact zones spaced apart from each other along the shaft 18, between the latter and the seal 19, as is the case thanks to the two balls 45 and 46. Indeed, in case of imperfect centering of the motor 17 inside the boltier, after mounting, a slight shift between the actual position of the shaft 18 and its desired position symbolized by the axis 18a, could cause slight leaks along the tree 18. It has been found that the presence of the two bumps 45 and 46

  spaced axially brought a satisfactory solution to this problem.

  On the other hand, a continuous circular groove 48 is made in said dynamic sealing portion 36 in the vicinity of the bead 45, to provide greater flexibility to the latter and to allow better permanent contact between said bead 45 and the rotating shaft 18 For the same

  Because of this, the peripheral bead 46 is defined in the vicinity of the end.

  mité an annular lip 49, substantially frustoconical.

  The intermediate portion of the seal located between said static and dynamic sealing portions comprises in particular a decoupling groove 50, extending relatively deep in the thickness.

  of the joint 19, to give more flexibility to this median part and to

  ter, as far as possible, that the deformations, necessary to the assembly, in one of the sealing portions engender harmful constraints in the other portion, likely to affect the effectiveness of sealing. It should be noted that in the embodiment described in FIG.

  circular groove 48 can also be considered as a throat for

  beach, given its relatively large depth.

  As mentioned previously, the protuberances 32 are

  projecting, after mounting, in the second chamber 16 are integral with the seal 19 and substantially distributed in circular symmetry around the axis 18. Their length is sufficient to come

  partially crashing against the engine frame 17 at the time of assembly.

  The all of these protuberances thus form a kind of spring interposed and mounted in compression between

  the remainder of the seal 19 and the motor 17, to immobilize the latter to the inte-

second chamber 16.

  Referring again to FIG. 1, it will be noted that a protective disk 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. In addition, a liquid discharge orifice 52 is formed in the side wall of this second chamber, this orifice being preferably located at the bottom of the housing, considering the normal position of

  illustrated in Figure 1 and substantially in line with

  Thus, in the event of a slight failure of the dynamic sealing portion 36, if liquid is able to penetrate into the second chamber 16 while flowing along the shaft 18, it is immediately deflected. to the side wall of the portion 27 and eventually be evacuated through the orifice 52, the rotor and the motor windings 17

  thus being protected from moisture.

  Of course, the invention is not limited to the embodiment of the device that has just been described. In particular, we have

  since the joint 19 as described fulfilled a threefold function:

  static sealing, dynamic sealing and elastic compensation

  putting immobilize the motor 17 inside the housing. It is obvious that it is perfectly possible to dissociate the last

  function of the other two. Thus, the protuberances 32 could be sup-

  awarded and replaced by any type of intercalated spring and

  mounted in compression between the seal and the engine. Similarly, protuberances

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  32 may not be molded in the same block of elastic compressible material as the seal 19, but form a separate piece

  bearing between the seal 19 and the engine 17. This means that

  vention covers all technical equivalents of the means involved

  if they are within the scope of the following claims.

Claims (15)

  1. Motor-driven pump device   type having a first chamber having an input of   quide and a liquid outlet and a discharge means, such as a wheel   vane or the like, forcing said liquid from said inlet to the   said outputaeand a second chamber housing an electric motor said discharge means being mechanically coupled to the shaft of said electric motor, characterized in that said first and second   chambers are adjacent and essentially separated by a joint in   elastically compressible material, comprising a sealing portion   static, substantially peripheral, and a portion of dynamic sealing   substantially central dynamic defining a tree passage traversed by said shaft of said engine.   2. Device according to claim 1, characterized by a spring means interposed and mounted in compression between said seal and said motor, to immobilize said motor inside said second bedroom.   3. Device according to claim 2, characterized in that said spring means comprises a plurality of protuberances of compressible material distributed substantially in circular symmetry. all around said tree.   4. Device according to claim 3, characterized in that said seal and said spring means are combined; said protuberances being integral with said joint and protruding   in said second chamber, towards said engine.   5. Device according to one of the preceding claims   characterized in that said static sealing portion comprises at least one outer peripheral bead9continuous, extending radially   outwardly relative to said shaft.   6. Device according to claim 5, characterized in that a continuous peripheral groove is made in said portion.   static sealing, in the vicinity of said peripheral bead.   7. Device according to claim 5 or 6, characterized in that said static sealing portion comprises two said outer peripheral beads spaced apart from each other   in a direction substantially parallel to said shaft.   8. Device according to one of the preceding claims,   preceding, characterized in that said static sealing portion   has at least one continuous bead extending parallel to the di-   Rectification of said shaft and directed to said first chamber; this bead being, after assembly, bearing against a shoulder defining the limit   of said first chamber, possibly via a ron- delle stop.   9.-Device according to one of the preceding claims,   characterized in that said dynamic sealing portion comprises at least one continuous, radially extending inner circumferential bead   inwardly of said shaft passage.   10. Device according to claim 9, characterized in that said dynamic sealing portion is provided with two aforementioned internal peripheral beads spaced parallel to each other   in a direction substantially parallel to said shaft.   11. Device according to claim 9 or 10, characterized   in that at least one aforementioned internal peripheral bead is defined   in the vicinity of the end of a substantially frustoconical annular lip.   Device according to claim 9 or 10, characterized   risé in that a continuous circular groove is practiced in said   dynamic sealing portion, in the vicinity of at least one bead internal route mentioned above.   13. Device according to one of the preceding claims   characterized in that at least one decoupling groove is practically   in the thickness of the gasket between said sealing portions static and dynamic.   14. Device according to all of the claims 12 And   13, characterized in that said continuous circular groove constitutes a aforementioned decoupling groove.   Device according to one of the preceding claims   characterized in that a protective disc, mounted on said shaft, is located in said second chamber between said seal and said motor and that at least one liquid discharge port is provided in   the side wall of said second chamber, preferably substantially   in the radial extension of said protective disk.