FR2568973A1 - EXHAUST VALVE FOR ROTATING PUMP WITH GEAR AND IMMERSION ENGINE FOR FUEL - Google Patents

Abstract

EXHAUST AND RELIEF VALVE FOR FUEL PUMP. A VALVE BODY 290 HAS AN INLET 300, AN OUTLET 296 AND A BORE 294 LOCKING A TUBING VALVE 302 WHICH FORM WITH THE BODY 290 AND A BALL 292 A RELAXATION PASSAGE 294-326 BETWEEN THE INLET AND OUTLET, A FIRST SPRING 306 REQUESTED THE BALL TOWARDS THE INLET AND THE VALVE TOWARDS THE OUTLET, THE BALL BEING ABLE TO COOPERATE WITH THE INLET TO FORM A BYPASS; THE VALVE IS CROSSED BY AN EXHAUST PASSAGE 314 WHICH THE BALL CAN CLOSE; A SECOND SPRING 304 STRIKES THE VALVE TOWARDS THE INLET TO NORMALLY CLOSE THE RELIEF PASSAGE 294, 326, THE PRESSURIZED STEAM THEN ESCAPING THROUGH THE BYPASS AND EXHAUST PASSAGES 314 UNTIL THE FLUID PRESSURE RISES THE RESISTANCE OF THE FIRST SPRING 306, THE BALL THEN CLOSING THE EXHAUST PASSAGE 314; THE PUMP FLUID PRESSURE RELAXES AND THE RELIEF PASSAGE OPENS WHEN THE FLUID PRESSURE EXCEEDS A PREDETERMINED VALUE TO PRESS THE VALVE TO THE OUTLET PASSAGE 296 TO OPEN THE RELIEF PASSAGE 294-326. APPLICATION ESPECIALLY TO INTERNAL COMBUSTION ENGINE SUPPLY SYSTEMS.

Description

- I -

  The present invention relates to fuel pumps and more particularly

  particularly fuel pumps with pressure reducing valves

and / or exhaust.

  So far, rotary electric pumps with a gear-type submerged motor, have not used exhaust valves to evacuate fuel vapors, because such a pump, when running at its normal speed , does not have a sufficient yield for pumping gases such as fuel vapors, in comparison with liquids

  such as petrol. It is common for any

  eg fuel gives off vapors of fuel. Rotary pumps

  which do not meet the manufacturing and measuring tolerances

  the tighter, and which have flatness and

  parallelism, can not self-initiate in the presence of an im-

  any load. However, in a rotary gear pump of the type having a check valve at the pump outlet to prevent

  any counter-current from the engine, such pressures of

  Fear continues to accumulate as the engine continues to spin and generate heat. The little fluid that penetrates through the intake of the pump is evaporated to the point where the pressure of

  steam drives the fuel through the intake, countercurrently.

  In pumping fuel in a rotary gear pump

  immersed motor, special conditions of

  to avoid excessive pressures in the closed feeder system for obvious reasons. Therefore, it is necessary to provide an exhaust valve. The dual function of evacuating

  steam under pressure until the liquid reaches the check valve.

  exhaust and to relax the pressure of the fluid beyond a pre-

  determined in the rotary gear type fuel pumps, is

unknown until now.

  The present invention is based on the fact that it is desirable

  to be able to combine the functions of an exhaust valve and a

  pet regulator to realize a single valve at low cost

  that can be used with a rotary type fuel pump

  grinding, in particular a submerged motor-type fuel pump.

  According to the present invention, there is provided a check valve

  exhaust and exhaust to evacuate the gases or vapors retained and which come from a fuel pump, and to relax the pressure of the

  fluid when it exceeds a predetermined value of relaxation.

  This exhaust and relaxation valve includes a ball that serves -2-

  shutter valve, a tubular valve through which a passage of

  surrounding the ball and can be closed by it, and a valve body provided with an inlet passage, an outlet passage and a valve bore located between these two passages and which contains the ball and the tubular valve. The tubular valve and the valve body form a normally closed exhaust passage between the inlet passage and the outlet passage. A first spring interposed between the ball and the tubular valve urges the ball towards the inlet passage and the tubular valve towards the outlet passage. The ball can cooperate with the inlet passage to establish a constantly open bypass passage for vapors, through the adoption of an imperfect ball seat,

  leak or bypass, arranged between the ball and the entrance passage, m9-

  me when the ball is in contact with this passage of entry. The tubular valve is traversed by an exhaust passage which can be closed by the ball. A second spring interposed between the tubular valve and

  the outlet passage, urges the tubular valve towards the passage of

  in order to normally close the exhaust passage. The pressure of

  steam is relaxed through the bypass passage and the passage of

  exhaust until the pressure of the fluid overcomes the resistance

  the first spring so as to move the ball so that it

  me the exhaust passage. The pressure of the fluid is expanded when the exhaust passage is opened by fluid pressure having a predetermined value, so as to move the tubular valve to the

exit passage.

  Therefore, one of the primary aims of the present invention is to provide a new and improved type of electric pump

immersed motor.

  Another primary aim of the present invention is to provide

  a fuel pump of the aforementioned type, comprising a combined valve of e-

escape and relaxation.

  In addition, the primary object of the present invention is to provide a fuel pump of the kind mentioned above, in which the exhaust and expansion valve comprises two shutter members or

  valves cooperating with each other in a common valve bore.

  On the other hand, the present invention also aims to provide an exhaust and expansion valve of the aforementioned type, in which the

  first shutter member applies against an imperfect seat or leakage

  te, so as to establish between the first shutter member and the seat a

  bypass passage, this first shutter member being displaced by

  -3 - to seal an exhaust passage formed through the second organ

  shutter as soon as the fuel pressure in the pump exceeds a

their determined.

  Finally, the present invention relates to an exhaust and expansion valve of the aforementioned type in which the second shutter member establishes a normally closed expansion passage in the bore of the valve and

  moves to open this relaxing passage when the pressure of

to reach a limit value.

  Referring to the accompanying drawings, in which

  FIGURE 1 is an end view of an embodiment of a pump.

  rotary-geared, gear-type electric submerged fuel pump in which certain features of the present invention have been incorporated

  FIG. 2 is an axial cross-section of the fuel pump.

  rant, and gear according to Figure 1, the section being made along line 2-2 of Figure 1;

  FIGURE 3 is a radial cross-section of the fuel pump.

  gear and gear according to Figure 2, the section being taken along the line 3-3 of this Figure 2;

  FIGURE 4 is a radial cross-section of the pump shown in FIG.

  Figure 2, the section being taken along the line 4-4 of this Figure 2; FIGURE 5 is an enlarged view. and exaggerated parts of the armature shaft and the internal wheel of the pump gear;

  FIGURE 6 is a cross-sectional view of the compression casing

  with a check valve and a safety valve of the

  FIG. 6A is a cross-sectional view showing a defective valve seat and a ball in the safety valve of FIG. 6, the sectional view of FIG.

  being taken along line 6A-6A of this Figure 6-

  FIGURE 7 is a sectional view of the pump shown in Figure 2, this section being taken in the direction of the arrows 7-7 of this Figure; FIGURE 8 is a partial plan view of a portion of Figure 2 showing the orientation of the discharge housing through the use of a locating tab disposed between the two magnets of the engine; FIGURE 9 is an exploded perspective view of the rotary electric pump shown in Figures 1-8;

  FIGURE 9A is a perspective view of a coupling device

  provided between the armature shaft and the inner wheel of the rotary pump 8973 shown in Figures 1 to 9;

  FIGURE 9B is a perspective view of a variant, but

  feasible, realization of the armature shown in Figures 7 and 9;

  FIGURE 10 is a partial sectional view of a portion of

  the embodiment of the pump outlet or discharge casing, where a safety valve and an oscillating bearing are shown for rotatably supporting an end portion of the armature shaft; FIGURE 10A is a perspective view of portions of a modified version of the support bearing and the pump discharge or discharge housing of Figure 10, o. we see the arrangement mortise and tenure of this door, designed to limit the circumferential rotation of the pad;

  FIGURE 11 is a perspective view of the movable member of the

  safety fart shown in Figure 10; FIGURE 12 is a plan view of an alternative embodiment of the pump or discharge outlet housing of Figure 10; FIGURE 13 is an underneath view showing the internal arrangement of the pump or discharge casing variant of Figure 12; FIGURE 14 is a cross-sectional view, but only of the variant of the discharge housing of Figures 10, 12 and 13, this section being taken along line 14-14 of Figure 12; FIGURE 15 is a sectional view made only through the discharge housing of Figures 10, 12, 13 and 14 taken along the line 15-15 of Figure 12, and

  FIGURE 16 is an exploded view, in perspective, showing some of the

  characteristics of the embodiment variant of the output casing

  pump or discharge, some elements of this casing being

felt in partial tearing.

  Referring first to FIGS. 2 and 9, there is shown thereon a rotating electric gear pump assembly for fuel or other fluid contained, for example, in a fuel tank.

  fuel (not shown) so as to supply fuel under pressure.

  a user device such as, for example, an internal combustion engine (not shown). Rotary motor-pump assembly or pump 10

  comprises a tubular shouldered boot 12 which encloses a crankcase

  14 of the pump, a rotary gear pump assembly 16, a cylindrical motor flow circulation jacket 17, a flange to

  discharge light 180 and an electric motor assembly 20

  sealed against a discharge housing 18 and supported between

  the intake casing 14 of the pump and the discharge casing 18.

  The shouldered and tubular casing 12 terminates at one end with an inwardly folded edge, designated 22, to form a seal against an annular shoulder 24 projecting radially outwardly on the discharge housing 18. Between this folded edge 22 and its opposite end, the shouldered tubular housing 12 has an internal bore 26 which forms a cylindrical chamber 28 intended to receive the motor itself, this bore 26 ending in a shoulder 32 o originates, in direction of said opposite end of the casing 12, a second bore 30 which in turn forms a cylindrical chamber 34 intended to receive the pump proper and which is followed in the same direction by a third smaller bore 36 which constitutes the chamber of intake 38 of the pump. This admission chamber 38 can

  be put in communication, according to the known mode, with a source of car-

  burant (not shown), for example via a coupler

  known type, a pipe and a filter (not shown).

  sented). Made of a single die-cast piece, for example in

  zinc, the intake and pump housing 14 has an external periphery

  a cylindrical form 40 which fits into the bore 30 for

  receiving the pump in the chamber 34 of the shouldered and tubular casing 12.

  The intake side end of the intake and pump housing 14 is

  mine by a tubular hub 42 which protrudes into the bore 36 and also into the inlet chamber 38 of the shouldered and tubular casing 12, and further has a stepped bore 44 whose structure and role will be further specified later . The cylindrical outside 45 of this tubular hub 42 is separated, by an annular space 46, from an annular spring washer 48 whose inner diameter 50 bears against a seat

  ring 52 which protrudes axially towards the inside of the casing é-

  and the tubular 12. The spring washer 48 is axially locked

  and radially by its diametrically outer portion 54 in a box

  56 is formed in the intake side face 58 of the intake and pump housing 14, just behind the cylindrical peripheral surface 40

of this housing 14.

  The entire electric motor 20 comprises an armature shaft 60

  having an end 62 on the input side and an end 64 on the output side, each

  end 62, 64 being rotated by means of a bearing or

  corresponding tubular sinet, or in ball bearings 66 and 68,

- 2568973

  slidably mounted on these ends and resiliently supported by respective O-rings 70 and 72, housed in a bore 74 of the intake and pump housing 14 and the other 72 in a bore 76 of the

  discharge housing 18. The tubular bearing or bearing 66 is lubricated

  and cooled by the fuel flowing through the chamber 38, while the tubular bearing or bushing 68 is lubricated through slots

  axial 75 distributed around the periphery of the bore 74.

  armature 60 is disposed substantially along the central axis of

  flow 78 which passes through the submerged assembly 10 of the motor and the rotary pump, its axial position being stopped by a thrust washer 182 biased against the seat 184 of this washer and which is part of the discharge plate or discharge lamp 180 of the pump, thanks to the magnetic attraction that occurs between the magnets 240 and 242, on the one hand, and the stack of armature t8les, on the other hand. The inlet-side bearing 66 is held in place by a shoulder 80 extending radially outwardly from the tubular bearing 66, and

  also to a shoulder 80 which extends radially outwards to

  pulling the tubular hub 42 so as to trap the O-ring 70

between these shoulders.

  Designed to rotate in the motor chamber 28, the electric motor

  20 comprises an armature 84 formed of a plurality of armature windings 86 wound in a plurality of magnetic tapes (not shown)

  provided with notches and attached to the press on a knurled part (not re-

  shown) of the armature shaft 60. Each armature winding 86

  two ends which end in the manner known to a

  88 which are rubbed into electrical contact and sliding two diametrically opposite collector brushes, designated 90 and 92, which are electrically connected to respective terminals 91 and 93 shaped caps. The brooms 90 and 92 are solicited against the

  manifold 88 along a translation axis 94 of the brushes by res-

  Broom spells designated respectively in 96 and 98.

  The end flanges 100 and 102, each provided with eight branches

  104 which extend radially from a central tubular hub 106 and are distributed at equal angular intervals, are respectively provided at the opposite ends of the plates of the magnetic circuit.

  and attached to the press on the aforementioned knurled parts of the shaft ---

  60. Along the outer axial side of each branch 104 it is

  seen a tongue 108 oriented axially and internally to the magnetic fields of the armature but without being in contact with these sheets. The axially outer side of each leg 104 has an outer surface

  curved along this branch so as to be in non-contact

  abrasive with the end turns of the armature windings 86 and at

  The central fibrous tubular hub 106 of the end flange 102 has an annular abutment shoulder 110

  No one extends radiaiemert towards the outside of this hub and ends axially

  by two jaws or drive splines 112 and 114, as shown more particularly in FIG. 9, in the form of curved and diametrically opposed sectors which extend radially inward of the

intake and pump housing 14.

  As will become more apparent with reference to Figures 2, 3 and 9 of the drawings, the intake and pump casing 14 has an internal recess 11, which opens on the armature 84 and defines on the one hand a cavity 118 for the rotor or pump gear, and secondly a central bore 120. The counterbore 116, the rotor cavity or central gear 120 are concentrically formed around offset axis 122, as best shown in FIGS. 3 and 9, with

  a predetermined radial offset 124 with respect to the central axis of flow.

  slow 7; along a first radial direction substantially

  pendicular to the axis 94 d-placement of the brushes. As we understand it

  will take more easily from Figures 2, 4 and 9 a depression 126

  shallow eb in the form of a circular arc and an opening of

  I form 128 are provided in the surface 130 of the recess bottom 116, approximately concentrically with respect to the central bore 120.

  best shown in FIG. 4, the inlet side 58 of the crankcase

  mission and pump 14 has a shallow axial depression 132, also in the form of a circular arc. A first inlet depression 132 in the side of the inlet 58 communicates with a first opening in an arc 128 provided in the surface of the bottom 130 of the binding 116, while a second depression in an arc 136 of the

  In addition, the inlet and pump casing inlet 58 communicates with

  The first and second intake depressions 132 and 136 cooperate to provide uncompressed fluid with the cavity 118 in the bottom 130O.

  the rotary pump 16 for the dual purpose of priming the pump and the

  bring in fluid to put under pressure.

  In the same cavity 118 of the pump 16 are housed a toothed wheel

  142 and an external gear wheel 144 of the gear pump,

  only in FIG. 3 in its assembled state. The inner -8- and outerwheels 142 and 144 have respective sets of inner teeth

  154 and external 156 pumping as well as intervals or hollows between

  teeth 158 and 160 which separate them. The internal teeth 154 of the wheel den-

  internal tee 142 of the rotary pump have a profile designed to co-operate or mesh, with pumping effect, with the other teeth 156 of the pump and the tooth cavities 158 of the external gear 144,

  while the teeth 156 of the external toothed wheel 144

  wire which enables them to hermetically mesh with the pumping effect, with the teeth 154 of the internal gear 142 as well as with the recesses 158 of the teeth of the same internal gear 142. The external gear 144 has a cylindrical peripheral surface 162 slid-housed and

  located in the recess 116 of the cavity 118 of the pump. The wheel

  dull 142 of the gear pump is traversed by a central bore

  164 which, as shown more clearly in Figures 2 and 5,

  carries a milled or conical inlet 166 opposite the surface 130 of the bottom of the recess-116 of the intake casing 14 of the pump. The internal diameter of the central bore 164 for controlling the internal wheel 142 is slightly larger (for example by 25 thousandths of a millimeter) than the external diameter of the armature shaft 60 which passes through this bore, while the length The axial axis of this bore 164 is calculated to be relatively shorter (for example 0.012 to 0.013 mm) than the internal diameter of this bore, so as to allow the armature shaft 60 to pivot slightly to the end. end to said internal control bore 164 and therefore to allow the O-ring 70 to automatically align the inlet end 62 with the inlet

  the armature shaft in the bore 74 of the tubular hub 42. This self-centering

  trage allows the armature shaft 60 low angular deflections

  relative to the central flow axis 78, the increased deflection angle

  with manufacturing and assembly tolerances.

  Beer. that can undergo self-centering with respect to the inner wheel

  However, as shown in FIGS. 3 and 9A, the armature shaft 142 of the pump, the armature shaft 60, nevertheless drives this internal wheel 142 of the pump. The inner wheel 142 has two jaw or entrained grooves 172 and 174 which protrude radially inwardly from

  this wheel to engage in the drive cavity 170 of the accou-

  plemrent. The drive splines 112 and 114, which form an accou-

  The control plating 177, as best shown in FIGS. 3 and 9A, have an enclosed angle of about one hundred and eighteen degrees (1180), and each of the driven flutes 172 and 174 forms an angle of about fifty-eight degrees. - 9-

  degrees (580). The four grooves 112, 114, 172 and 174 consequently have

  a total circumferential clearance of approximately eight degrees (80). This angular clearance is sufficient to facilitate the assembly of the drive coupling but also to tolerate a slight axial misalignment thus allowing the end-to-end self-centering of the drive shaft.

  60 relative to the internal gear 142 of the pump.

  To complete the assembly of the rotary electric pump 16 is provided a discharge plate or discharge ports 180 and a thrust washer 182 Ultem Teflon loaded. The discharge plate 180 of the pump has an annular abutment surface 184 in the center of an annular zone forming a recess on the outlet side 186 and a bore 188 which passes through this plate and whose diameter is sufficient to allow the grooves 122 and 114 of the central and tubular fibrous hub 106 to pass through this

  bore with a suitable clearance (for example of the order of 0.12 to 0.13 mm).

  The annular outlet plate 180 of the pump furthermore has an additional

  outer peripheral face 190 and an annular radial groove 192 formed in the exit-side angle of this plate. This peripheral surface 190 is housed in the external bore 26 of the tubular shoulder housing 12 and bears against the face of the annular shoulder 32 that it presents,

  which ensures the correct radial and axial positioning of the

  annular setting 17 for the circulation of the magnetic flux of the engine. The thrust washer 182 is biased against the abutment surface 184 of the delivery plate 180 of the pump by the annular shoulder of

  stop 110 of the central hub tubular 106. The thrust washer 182 com-

  carries two diametrically opposite internal grooves or teeth 193a and 193b of curved shape, oriented radially inwardly so as to

  to engage and drive the splines 112 and 114 of the central tubular hub

106.

  On an axial side facing the internal gear wheels 142 and

  144 of the pump, the discharge plate 180 of the pump

  also feels a depression in the shape of an arc of a circle 196 which corresponds to

  substantially weighted the shape and position of the arcuate depression 126 and the arcuate opening 128 provided in the bottom surface 130 of the recess 116 of the cavity 118 of the pump in the inlet end of the housing intake 14 of the pump. To ensure correct priming and other desirable characteristics of the pump, the opening 128 in a circular arc and the depression 196 also in an arc communicate with each other through bores respectively.

- 10 -

  and 188, with respective radial grooves 200 and 202, as best shown in FIGS. 2 and 9. In addition, to provide an appropriate outlet lumen for the pumped fluid at the required pressure in the cavity 118 of the pump rotating, the annular outlet plate 180 of the pump is traversed by the arcuate opening 198 whose shape and position correspond to those of the arcuate depression 126. To properly dispose of the discharge plate 180 of the pump

  in the circumferential direction with respect to the intake and pump housing

  14, two positioning pins 204 and 206 are fixed on this plate.

  180 and project on an annular radial surface 208 so as to engage in corresponding holes 205 and 207 which pass through a

  radial annular surface 209 of the discharge plate of the pump.

  The pressurized fluid coming out of the arcuate opening 198 of the output of the pump discharge plate 180 is guided from this opening and protected against the baffle effect produced.

  by the armature 84 thanks to a device 210 with a tunnel and reinforcement for aiding

  motor devices, visible in particular in Figures 7 and 9. This device 210 tunnel and frame for motor magnets consists of a first

  channel or flow passage 211 protected against the action of turbulence

  This channel 211 extends substantially over the entire axial length of the motor chamber 28 between the discharge plate 180 of the pump and the annular shoulder 24 of the discharge casing 18. shape of an inverted jumper, the device 210 with tunnel and frame for magnets motors presents

  a central portion 212 forming a bridge delimited by two wings wings

  The central bridge portion 212 is slightly convex, looking from the outside of the pump, to conform to the peripheral contour of the armature 84, while the two wings 214 and 216 are radially oriented. outward from this

  central portion 212 in the form of a bridge, to be applied against a sur-

  internal peripheral face 218 of the cylindrical magnetic sleeve 17

  for the circulation of the magnetic flux of the motor. This shirt 17 is

  also extends over almost the entire axial length between the delivery plate 180 of the pump and the annular shoulder

  outside 24 of the discharge casing 18.

  To allow a virtually unimpeded flow of the fluid under pressure coming out of the arc opening 198 and penetrating

  in the tunnel device 210 and magnet armature, while maintaining this device in a well-defined circumferential position,

  The input end 222 of this device is provided with two tabs

  axially protruding projections 224 and 226 spaced apart in the circumferential direction.

  In order to provide a gap 228 for the entry of the fluid, the projecting tongue 224 terminates in a perpendicular edge 230 intended to abut directly against the radial annular surface.

  209 of the discharge plate 180 of the pump. The other tongue

  lante 226 ends with a section cut out in bayonet 232 which forms

  on the one hand an abutment 232a abutment intended to wear against the sur-

  radial annular face 209, and secondly a finger 232b which enters through the outlet side into the hole 207 so as to correctly orient the discharge plate 180 of the pump relative to the intake housing

  of the pump, as indicated above.

  The wings 214 and 216 of the device 210 with tunnel and reinforcement for

  motor magnets cooperate with two legs 234 and 236 oriented to the op-

  placed in the circumferential direction and which

  on the respective protruding tongues 224 and 226 so as to maintain the correct position of the two crescent-shaped motor magnets 240 and 242 in both circumferential and axial directions relative to the armature 84 As it stands out more

  7, 8 and 9, each crank-shaped motor magnet

  240 and 242 is delimited in its axial length by first and

  second juxtaposed axial faces 240a, 240b and 242a, 242b, and each

  mant 240 and 242 is delimited at its input and output ends by

  respective end faces 240c, 242c and 240d, 242d.

  During assembly, the device 210 with tunnel and magnet reinforcement is

  first engaged so that the finger 232b is housed in the hole of re-

  perage 207 of the discharge plate 180 of the pump. Then, the engine magnets 240 and 242 are placed in such a way that their axial faces 240a and 242a respectively abut against the wings 214 and 216, while the end faces 240c and 242c abut against the tabs 234 and 236. To ensure the correct spacing between the magnets 240 and 242, on the one hand, and the discharge light plate 180 of the pump, on the other hand, while providing a second flow channel 211a between these magnets, is then inserted a compression spring 246 of steel wire, bent in a V-shape, between the second set of juxtaposed axial surfaces 240b and 242b, in order to urge the axial surfaces 240a and

  242a in the circumferential direction against wings 214 and 216 of the

  210 with tunnel and magnets frame.

  Finally, the outlet or discharge casing 18 is engaged in the

- 1 256893

  12. The circumferential orientation of this discharge casing 18 is determined with respect to the tunnel device 210 and magnet reinforcement, as clearly shown in FIG. 8, by a curved sector 248 which projects between the axial surfaces. 24Ob and 242b of the crescent-shaped motor magnets 240 and 242. A pump outlet tubing 250 is thus aligned through the discharge casing 18 along the same axial plane which intersects the center of the magnet tunnel and magnet device 210 and the center of the light.

  198 in an arc that passes through the pump outlet plate 180.

  The aforementioned correct circumferential orientation of the housing of

  flow 18 relative to the tunnel device 210 and magnet armature allows a smooth and unimpeded flow of pressurized fluid therethrough directly from the outlet lumen 198 and through the first flow passageway 211 until the

  pump outlet lumen 252 of the discharge casing 18.

  According to the results of experimental tests carried out in

  In normal conditions, it has been found that the apparatus described above substantially improves the efficiency of the pump. In comparison with submerged pumps

  similar in size and capacity, the electric pump assembly

  mergée described above provides the required fluid pressure at substantially increased flow rates while appreciably reducing the

  induced current consumption, for example, in a typical application

  characteristic of a conventional passenger car internal combustion engine, it has been found that the flow rates or flow rates are uniformly increased to the extent of at least 11i.

* liters per hour, whereas the corresponding armature currents decrease

at least 12 percent.

  Part of this improvement can be attributed to the simple fact of providing an axial flow channel, such as

  realize the magnet reinforcement device 210a shown in Figure 9B.

  This magnet armature comprises a central portion 212a forming a bridge, which abuts against the annular sleeve 17 circulating the motor flow and is delimited laterally by wings 214a, 216a which

  tilt radially inwards, that is to say towards the armature 84.

  However; such a reinforcement would have the effect of allowing the formation of armature turbulence to the point of generating radial-oriented hydraulic spirals in the flow channels 211b. However, this turbulence would tend to reduce the effective cross section of the axial flow channel 211b to a small portion of its cross section

_ 18 _

  real. To avoid these spirals and the aforementioned turbulence, while increasing

  substantially extending the cross-section, the magnetic tunnel and magnet device 210 in accordance with the preferred embodiment of the present invention is designed so that the central bridge 212 of this device protects the flow through the device against the effects of turbulence due to the presence of the armature. In case we wish to bring

  other improvements to this construction in order to avoid spinnings

  hydraulics induced by an orientation in the channel 211 due to

  its tightening of the flow imposed by the circumferential width-

  In this channel, channel 211 could further be subdivided into several sub-channels formed by several pipes or grooves. Such subchannels would be likely to achieve a steady and constant flow of

  fluid, which would greatly increase the cross-sectional area

  of the flow in relation to the real cross-section of the

channel.

  As shown in FIGS. 1 and 6, this outlet or discharge casing 18 of the pump, made of a molded plastic material, for example of Ultem, comprises a pump outlet valve 250 whose discharge pipe 252 is intended to be connected to

  an internal combustion engine. This discharge pipe 252 com-

  carries an internal axial outlet passage 251 provided with a seal member 253 with a diametrical notch, which fits into an exit bore

  254 so as to trap a ball 255 which constitutes the movable member

  the valve proper 256, the discharge housing 18 comprises a

  annular seat 257 which cooperates with the ball 255 so as to constitute

  kill a one-way check valve that prevents any return of

  between the engine and the pump. To allow normal circulation

  male, that is to say in the direction of feeding, between the pump 10 and

  the motor, the discharge pipe 252 ends with four teeth co-

  258 which form grooves 259 between them and which normally limit

  wrongly the outward movement of ball 255 of the flap, while

  that the grooves 259 allow the flow of fuel to the outside.

  the pump between these teeth and the ball. The cone angle 258 of the conical teeth is calculated to serve as a housing for the ball 255 while pocketing its oscillating movements when certain flow rates are reached. A new characteristic of the "submerged" motor-pump assembly according to the present invention lies in the presence of a valve 260 for exhausting the vapors in the discharge casing 18, as well as, at best, the 2568973 spring at best Figures 6 and 6A. This exhaust valve 260 is located in a diametrically opposite position relative to the valve of

  outlet or discharge 250 and includes a ball 262 which constitutes the

  movable valve of the valve 260 and is housed in a valve bore 264 formed in an expansion pipe 266 traversed by an exhaust passage

  268 and provided with an annular flange 270 which is applied against a surface

  this annular 272 of the discharge housing or discharge 18. A compression coil spring 274 constantly tends to spread the ball 262

  a shoulder 276 which surrounds an internal collar 278 of the tubular

  266 relaxing while urging this ball against a seal im-

  perfect formed by a square seat 280 (particularly visible in Figure 6A) at the end of a relief bore 282 formed in the output housing 18. When the ball 262 is in contact with the square seat 280, it does not is that by four points 284a, 284b, 284c and 284d,

  this provision making it possible to obtain appropriate passages from

  286a, 286b, 286c and 286d. With this arrangement, any pressurized steam generated in the entire rotary electric pump

  16, especially during the self-priming of the pump, can escape

  to all of these appropriate passages 286a, 286b, 286c and 286d,

  that the liquid reaches the discharge or outlet side of the pumping elements and the relief bore 282. Then, the fluid pressure

  which applies to ball 262 succeeds in overcoming the solicitation

  pick on this ball by the compression spring 274 in order to apply

  the ball 262 against the inner flange 278 formed at the inner end

  of the expansion tube 266, which closes the valve passage

  268 and allows the normal operation of the pump and the output of the

  fuel through the discharge housing 250.

  The square seat 280 incorporated in the exhaust valve 260 of the vault

  fear described above may be replaced by any other suitable seat of non-circular or imperfect shape, including, for example, valve seats having a partially circular shape and consisting of

  circular valve seats, crossed by axial grooves.

  Another application of an imperfect seat for a valve consists in making a combination between such a seat and an expansion valve 290, as shown in FIGS. 10 and 11 in an alternative embodiment of the discharge casing 19. As shown in FIG. more clearly from these Figures, a ball 292 is housed in a bore 294 formed in the discharge housing 19 o it forms a valve chamber or valve, designated 295. One end of this bore 294 communicates constantly

2568973-

- 16 -

  with a vapor exhaust passage 296 formed through the end of the discharge housing 19, while the other end of this bore

  294 is fixed in any suitable manner, for example by super-welding

  sonic, to a valve seat member 298 traversed by a central passage

  tral 300 which communicates constantly with the chamber 28 of the engine. This central passage 300 opens into a valve seat 301 of elongated shape, consisting of a recess with a width equal to the diameter of the central passage 300 and a length equal to twice this diameter. When in contact with the seat member 298, the ball 292 may also contact the elongated seat 301 at one or the other of two diametrically opposed points if it is placed in the center of the seat. this seat, or by contact in a semicircle if it is shifted towards one or the other of its two extreme sides. In one case as in the other, there is a shunt passage that remains constantly open between the

  ball 292 and seat 301 elongated.

  In the valve chamber 295 formed by the bore 294 and the valve seat 298 are also housed an exhaust valve 302, of tubular shape, a first compression coil spring 304, a second compression coil spring 306 and a seal sealing ring 308. One end of the first spring 304 is pressed against an annular shoulder 310 formed in the vapor outlet passage 296, while the other end of this spring 304 is biased against an upper annular surface 312 formed at the top of the retaining valve 302 so as to surround a central exhaust passage 314 which passes through this valve. The first coil spring 304 urges the tubular valve 302 so that it normally bears against its seat and seals

  thanks to its O-ring 308, which normally bears against a surface

  this sealing ring 316 provided on said valve seat member

  298 around the valve seat 301 of elongated shape of this element. Lors-

  that the exhaust tubular valve 302 is normally urged to

  O-ring 308 is used to seal the sealing ring 316 against the annular sealing surface 316, thereby providing a normally open bypass passage between the central passage 300 of the valve seat 298 through the passage. central exhaust 314 of the exhaust tubular valve 302 and the exhaust passage of the vapors 296 of the exhaust or discharge casing 19. This bypass exhaust passage is closed, as will be described later, when the motor-pump assembly 10 produces a fluid pressure greater than a maximum and predetermined expansion value in the form of a liquid which acts

- 1s -

on the ball 292.

  The tubular exhaust valve 302 also has a

  tubular bore 318 provided with splines and a tubular bore 320 at one end, which passes the outer diameter of the ball 292 and has an annular seat 322 in the form of a flange which makes

  protruding inwardly at the other end of this bore.

  One end of the second helical compression spring 306 surrounds the ring-shaped annular seat 322 while the other end of the second spring 306 acts against the peripheral surface of the ball 292 in order to apply it against the seat 301. elongate. However, when the pressure of the fluid that is produced in the pump 10 exceeds the maxingal exhaust pressure, this excessive pressure overcomes the stress that the second compression coil spring 306 exerts on the ball 292 and moves it to the ring seat. 322, on

  the ball is then applied as soon as the pressure of the pump de-

  passes the predetermined maximum and predetermined exhaust pressure. At pumping pressure values which are between the maximum pressure

  aeration and a predetermined exhaust pressure, the ball 292

  me the planned passage for the fluid between the passage of the central seat 300

and the exhaust passage 296.

  To obtain an exhaust capacity or condition when the pump is subjected to a fluid pressure that exceeds a predetermined exhaust value, the axial periphery 324 of the exhaust valve 302 has six axial splines 326a, 326b, 326c 326d, 326e. and 326f, who

  extend radially outwards and are distributed at intervals

  equal angular valleys around the tubular portion 318. These flutes

  326a to 326f also serve to guide and center the exhaust valve.

  302 relative to the bore 294. Each of the axial splines 326a to 326f is contiguous with a corresponding tongue 328a to 328f forming

  spacing and which rises axially from and around the upper face

  312 and the central exhaust passage 314 which passes through this face 312. The tongues 328a to 328f can abut against a surface

  annular-stop 330 at the top of the internal recess of the housing of re-

  19, so as to space axially the remainder of the valve of

  exhaust 302 with respect to this annular surface 330 around the pas-

  exhaust pipe 296. Flutes 326a to 326f and tabs

  328a to 32Sf form passages or grooves 332a to 332f re-

  parts at equal angular intervals around the axial periphery 324 of the exhaust valve 302. The grooves 332a to 332f cooperate

- 1 2568973

  with the exhaust passage 296 so as to ensure constant communication of the entire space between the bore 294 and the axial periphery 324 of the exhaust valve 302, on the one hand, and the

  exhaust passage 296 vapors on the other hand. However, this space

  it does not communicate with the central passage 300 until the moment when the

  pump generates excess pressure, thus overcoming the

  elastically exerted by the first coil spring 304 against the O-ring 308 to move the exhaust valve 302

  of the ring seat 316 to bring it closer to the annular surface of bu-

  330. This excessive pump pressure therefore tends to distance

  seal the 308 o-ring exhaust valve, thus

  of the annular surface 316, which opens a pathway through

  332a to 332f from the central passage 300, passing through the

  294, the axial periphery 324 of the exhaust valve 302, through

  to the grooves 332a to 332f to finally exit through the passage

exhaust 296.

  Other variants of embodiment of the pump 10, that show the

  Figures 10 and 10A, reside in the construction of different tubular rings

  340 and 340a, which have a convex outer surface in

  the longitudinal direction, this surface having the appearance of a cap or neck

  342 of the outflow housing 18 to allow a slight self-centering end to end of the armature shaft 60. To restrict the tendency of the armature shaft 60 to

  this tubular ring to rotate in the bore 344, there is provided a dis-

  positive anti-rotation in the form of a set 348 with key and groove

  wherein a groove 348a formed in the tubular ring 340 is

  narrower and radially slightly deeper than a 348b key. Another characteristic of the immersed motor-pump assembly 10 lies in the use of an arrangement that is otherwise available in the variant embodiment of the discharge casing 19, in combination with complementary passages formed in this casing, for cooling

  and lubricating a portion of the tubular ring 340 between the point of contact

  tact of the larger or protruding portion 346 and the bore 344, on the one hand, and the upper surface or top 360 of the discharge housing, on the other hand. As will become more apparent in FIGS. 10 to 16, and especially in FIG. 14, there is provided a lubricating and cooling system 350 in the form of a circulation network 354 between a projecting cap 352, a cylindrical surface

- 1 -2568973

  89 of the collector 88, the bore 344 and two peaks 356 and

  358 for respectively supporting the brushes 90 and 92.

  As further apparent from FIG. 12, the protruding cap 352 supports the discharge valve 250 and the manifold 290 for receiving the exhaust valve line, and this same cap 352 includes the flat top 360 which supports the tubing 250 and the pipe 290 for receiving the pipe of the exhaust valve, while also having two side walls

  362 and 364 and two curved end walls 366 and 368.

  The flow network 354, seen in the transverse radial plane of

  Figure 13, has substantially the shape of the Roman numeral X. More partic-

  In particular, the circulation network 354 comprises four branches 370,

  372, 374 and 376, each having the shape called dog paw. These branches

  each communicates with the axial length of the bore 344 as well as with an annular recess 378 which surrounds a flange 380 which projects into the bore 344 from the end or top wall 360. Each branch comprises a portion 370a, 370b, 370c and 370d and each portion 370a to 370d is substantially parallel

  at one of the sidewalls 362 and 364, the parts of branches of

  side king 370a and 372a laterally covering, in essence, the exhaust valve 290 while the side wall branch portions

  374a and 376a cover laterally, in essence, the pressure tubing

  250 of the pump. Each of the branches 370, 372, 374 and 376 also comprises a portion of the respective radial branches 370b, 372b, 374b

  and 376b each terminating in a wall branch portion of

  with respective radial notches 370c, 372c, 374c and 376c formed circumferentially through a bore wall 382

  which actually constitutes the bore 344.

  Brush holder crates 356 and 358 include an element

  curved crown, crown or wall 356a and 358a rotated

  inwards, the curved crown of crest 356a being delimited

  It has two sidewalls 356b and 356c, while the curved crest wall 358a is delimited by two radial ridge sidewalls 358b and 358c. The side walls of radial ridge 356b, 356c, 358b and

  358c of each set are radially separated by an included angle of

  90 and, together with the respective crest crown walls 356a and 358a, extend axially with respect to a curved crest wall recess 384 to a depth corresponding to the axial width of the collector 88. The crowns or walls of curved crest 356a and 358a are slightly larger in diameter than the collectors

  88 in order to allow a game to remain between them, which

  proper handling of the collector brushes. Bore 344 starts at

  the depth of the recess 384 of the curved crust and extends axially-

  to the inner face 361 of the top wall 360. When the bore begins below the brush cups 356 and 358, a curved or mortise opening in an arc of a circle is formed which

  angle of about 90 degrees between the side walls of the rim

  opposing brush cups 356 and 358. In other words,

  there is a circumferential interruption of about 900

  the radial side projections 356 and 358 have an axial distance from the manifold 88, and there is a similar circumferential interruption between the side walls 356c and 358c of these radial projections. Assuming that the armature 84 is excited to rotate in

  anti-clockwise (looking at Figure 13), the peripheral surface

  cylindrical 89 of the manifold 88 will cause fluid by capillary

  this fluid being taken as a result of the rotation of the collector at

  the location of the radial notches 376c and 372c which respectively

  the sidewalls 356c and 358b of the radial crates, then projected or cut against the sidewalls 358c and 356c, respectively, radial notches 374c and 370c. The fluid thus withdrawn at the location of the diametrically opposite side walls 356c and 358b is thus launched at a speed greater than that of the fluid which is striking, and which is collected by the side walls 356b and 358c diametrically opposite. This difference in speed has the effect that the fluid in the radial grooves 370c and 374c moves more slowly and therefore is subjected to a higher pressure than the

  fluid that is in the radial notches 372c and 376c. A pressure

  similar differential approach could be obtained with other

  for example using blades or other form of resistance

  at discharge, the peak walls according to the preferred embodiment

  written above having the dual role of supporting brooms and also

  to produce the necessary differential pressure.

  In any case, the differential pressure created by the resistance forces of the manifold periphery 89 acting on the fluid at the indicated location of the radial crestal sidewalls produces an effect.

  d pumping fluid into the branch portions 370a and 374b. This ef-

  fluid pump is directed axially outwards, against

- 20 -

  the inner surface 361 of the top of the discharge casing 19, and then

  dialing inwards in the annular cavity 378, then axially

  around the tubular ring 340, then radially outwardly from the annular recess 378, to finally return through the opposing radial limb portions 372b and 376b. In other words, the cylindrical peripheral surface 89 of the collector, the support crates 356 and 358 of the brushes and the circulation network 354 constitute two parallel pumping chambers or circuits, separated by the collector 88 but connected by the annular cavity 378. The differential pressures produced by the difference between the respective velocities obtained at the indicated lateral walls of the radial ridges produce two inlet currents and two fluid outlet currents at these locations, the two

  currents combining with each other to cool and lubricate the bushing.

  340 and the bore 344. Through this cooling and lubrication, it has been found that the useful life of the ring

  upper tubular 340 was considerably extended by

  duration of the same level without this cooling or lubrication

  cation. In addition, we obtain mu acceptable greasing by providing only one

  only circuit communicating with the annular cavity 378 connected to the

  upper end of the tubular ring 340 above the point where its crown 342 is in contact with the bore 344. This lubrication would be

  however, less than that provided by the double-branch circuit

  rallies represented here. Similarly, a slight flow of fluid could

  to ensure sufficient differential pressure between the inlet and the outlet of the annular cavity 378, without the benefit deriving from the structure

  res to generate additional pressure.

  Although the best mode of realization has been described

  by the inventor for the implementation of the present invention, he

  it is clear to any specialist in the art that can be

  different modifications, variants and equivalences without departing

  however, basic principles of the invention.

- 21 -

RE V E N D I CA TI 0 NS

  1. Exhaust and expansion valve for fuel pump, des-

  used to evacuate gases or vapors under a lower pressure than

  fluid and to relax this pressure of the fluid when it exceeds a

  their predetermined, this exhaust and expansion valve being characterized in that it comprises: a) a ball (292) forming a first shutter member;

  b) a tubular valve (302) forming a second obturator

  and axially traversed by an exhaust passage (314) to be closed by the ball (292);

  c) a body (290) comprising an inlet passage (300), a step

  output shaft (296) and a valve bore (294) disposed therebetween

  passages, this bore (294) containing the ball (292) and the valve

  tubular pe (302), this tubular valve (302) and the cooperating body (290)

  between them so as to define a relaxation passage (320 - 326) between

  the input passage (300) and the output passage (296); (d) a first solicitation (306) interposed between the

  ball (292) and the tubular valve (302), this first means of solicitation

  (306) acting to resiliently bias the ball (292)

  to the inlet passage (300) and the tubular valve (302) to the

  output shaft (296), the ball (292) being further engageable with said inlet passage (300) for establishing between these two elements a bypass passage for the steam when the ball (292) comes into contact with said inlet passage (300), while the tubular valve (302) has an exhaust passage (314) closable by the ball (292), and e) a second biasing means (304) interposed between the tubular valve (302) and the outlet passage (296), said second biasing means (304) acting to resiliently bias the tubular valve (302) toward the inlet passage (300) to close the

  relief passage (320 - 326) between the inlet passage (300) and the step

  exit sage (296); (f) the arrangement is such that the vapor under pressure is discharged through the above-mentioned bypass passage and

  exhaust passage (314) from the tubular valve (302) to the

  when the fuel pump generates a sufficient fluid pressure to overcome the resistance of the first biasing means (306) and thereby allow the ball (292) to plug the exhaust passage (314), which relieves the pressure fluid when said detent passage

- 22 -

  (320 - 326) is open because the fluid pressure exceeds a

  their predetermined relaxation, in order to urge the tubular valve (302) towards the outlet passage (296) and thus to open the passage of

relaxation (320 - 326).

Claims (7)

2. Exhaust and expansion valve according to Claim 1,   characterized in that the tubular valve (302) encircles the ball (292).   3. Exhaust and expansion valve according to Claim 2,   characterized in that the tubular valve (302) comprises nipples   axially oriented vases (326 - 326f) and circumferentially separated   by grooves (332a - 332f) so as to effect said passage of   attempted. 4. Exhaust and expansion valve according to Claim 3, characterized in that said inlet passage (300) is encircled by a non-circular seat (301) and that the ball (292) bears on this seat of way to allow some leak to form said passage   in derivation between these elements.   An exhaust valve according to claim 4, characterized by   the fact that said non-circular valve seat (301) is square in shape.   6. Exhaust and expansion valve according to Claim 4,   characterized in that said non-circular seat (301) is of   oblong with a width equal to the diameter of the entrance passage (300)   and a length greater than this diameter.   7. Exhaust and expansion valve according to claim 1,   characterized by the fact that the first solicitation means (306) com-   takes a gravitational element that cooperates with a preferred orientation of the ball axis (292) when this axis is in close proximity   of the vertical axis relative to the ground.   8. Exhaust and expansion valve for a pump for pumping a fluid capable of generating a vapor pressure, this pump being furthermore capable of operating in a starting condition such that said vapor pressure is less than a pressure of fluid, and also in a pumping condition o said pressure of   fluid is between the vapor pressure and a pressure of   te, this exhaust and expansion valve being characterized by comprising: a) a valve body (290) having an inlet passage (300), an outlet passage (296) and a bore of valve (294) disposed between these passages along a valve axis, said valve bore (294) having - 23 -   an entrance end that surrounds the inlet passage (300) and an   exit trough that surrounds the outlet passage (296), the valve body (290) being further provided with a first valve seat surface (316) at said inlet end and a stop surface valve (330) at said outlet end; b) first and second shutter members (292, 302) accommodated in said valve bore (294) and movable along said valve shaft, the first shutter member (292) being movable between the inlet passageway (300) and the second shutter member (302), while said second shutter member (302) is movable between the first valve seat (316) and said valve stopping surface (330); c) the first shutter member (292) for cooperating with the first valve seat (301) surrounding said inlet passage (300) leaves between these elements a bypass passage or   vapor leakage when the first shutter member (292) carries   be its seat (301); d) the second shutter member (302) has a portion which   constitutes its summit, which is crossed by a passage of   (314) to allow escape of vapors passed through said bypass passage and a second sealing surface (322)   surrounding said exhaust passage (314), the first closure member   driver (292) engageable with said second sealing surface (322) for providing a first seal therewith; the second   shutter member (302) further comprises a third sealing surface   (308) which surrounds the first obturator member (292) and is   pierce with the first sealing surface (316) to make a second seal! said second shutter member (302) and the valve bore (294) providing therebetween a normally closed expansion passage between the second seal and said exit passage (296); e) mu first biasing means (306) interposed between the first and second shutter members (292, 302) and exerting a first   resilient bias between these members so as to achieve said first   first seal until said fluid pressure is reached, this   the pressure of fluid then surmounting this first elastic stress   to move the first shutter member (292) toward the second   shutter member (302) and closing said exhaust passage (314), and f) a second biasing means (304) interposed between the   valve body (290) and the second shutter member (302) to apply   a second elastic biasing between these members for the purpose of producing said second seal until said fluid pressure reaches a predetermined expansion value, thereby   this pressure of the fluid to overcome said second solicitation   to move the second shutter member (302) toward said sur-   stop face (330) to thereby open the first seal and relax the   fluid pressure through said inlet passage (300) and said relaxing sage (294);   g) the first and second closure members (292, 302) cooperating   thereby interact with each other to relax the vapor pressure until the fluid pressure acts on the first shutter member (292) to close the exhaust passage (294) and also, normally, the vent passage (300), until the instant when said pressure of   fluid reaches said predetermined expansion value.   9. Exhaust and expansion valve according to Claim 8, characterized in that the first shutter member comprises a gravitation means which cooperates with a preferred orientation of said valve axis which is in the vicinity of the vertical axis relative to on the ground.