JPS60230578A - Immersion motor rotor fuel pump - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to fuel pumps, and more particularly to fuel pumps in which the armature of a drive motor is immersed in the fluid pumped by the pump. It relates to different types of fuel pumps.

PRIOR ART One of the factors that limited the life of conventional immersion motor fuel pumps was the wear life of the slotted key joint provided between the motor drive member and the pump driven member.

Such wear is particularly important when the pump is a gerotor pump. This is because the wear affects the gap and wear of the teeth of the pumping gear.

Moreover, such slotted key joints produce noise, which increases with increasing wear.

Another problem with immersion motor pumps is that the rotating armature of the motor causes turbulence in the fuel flow, and that turbulence reduces the flow rate, thus reducing the This actually increases the armature current required to deliver the flow, and the turbulence also undesirably increases the temperature of the fuel.

Another problem with gerotor-type fuel pumps is that the high precision required for the gerotor pump's gear components also requires high precision for other parts of the pump, such as the armature shaft and the bearings that support it. It is to be done.

If their accuracy is higher than is normally required, the overall cost of the pump increases.

Yet another problem with gerotor pumps is that they are relatively expensive to manufacture due to the large number of precision parts used. Also,
Other components, such as the motor magnets, must be joined in place with precise spacing and proper alignment relative to the roots. A failure occurs when the armature and the magnet come into contact, and another occurs when the pump end of the root and the pump outlet plate come into contact. In addition, it uses a surface dog joint, which has not been previously used in gerotor fuel pumps, which significantly improves the wear characteristics of the connection between the armature shaft and the driven member of the pump, while at the same time reducing the wear characteristics of other parts. The precision required for these parts can be lowered, and the structure of those parts can be made more solid, so that their lifespan can be extended.

The present invention also provides an axial flow path between the magnets of the motor to allow fuel to flow between the magnets and to strengthen the structure of the magnets.

Additionally, the present invention provides for low cost pump assembly and improved performance while providing zero cost savings by using a pump case that is configured to properly align the inlet housing with the pump and motor members. A sealing device such as a ring is used to provide the necessary sealing.

In accordance with the invention, an integral cylindrical pump case includes an integral inlet and pump housing, a gerotor pump outlet plate,
surrounding the motor flux ring and the shoulder of the outlet housing;
and the pump case has a cylindrical inlet coupled to a fuel source. The inlet and pump housing houses the inner and outer pump gears of the gerotor pump, cooperates with the outlet housing to rotatably support the end of the armature shaft of the immersion motor, and connects the gerotor cavity and the outer pump. Allows for slight self-alignment or centering between the ends of the armature shaft with respect to the inner pump gear which is accurately aligned with the gear. The armature winding is wound around the fingers of a fiber hub that is fixed to the armature shaft. The armature shaft has a pair of drive dogs on diametrically opposite sides thereof.

The drive dogs extend axially and fit into coupling cavities provided in the inner pump gear.

A pair of driven dogs on the inner pump gear extend radially into the coupling cavity and are thereby coupled to drive dogs on the shifter hub.

A thrust washer attached to the fiber hub against the thrust shoulder also has a pair of driven dogs. The driven dogs extend radially inwardly and are coupled to and driven by the drive dog of the fiber hub. The thrust washer contacts the appropriate thrust surface of the pump outlet plate which serves to surround the inner and outer pump gears within the gerotor cavity provided in the artificial shaft and pump housing. Pressurized fluid directed through the pump outlet plate is passed through a flow passageway formed between a pair of circumferentially juxtaposed 111III linear surfaces of a pair of crescent-shaped motor magnets. Such an axial surface is separated in the circumferential direction by a retaining device inserted in its rl. The retaining device has a central bridge portion. Its central bridge section radially contacts the Danto ring of the motor and is limited by a pair of legs that open radially inward toward the Ichiisogo, and is bounded by a pair of crescent-shaped motor magnets. Contact an axial surface. between another set of circumferentially juxtaposed axial surfaces of the motor magnets;
A compression spring is inserted to press the axial surface of the former against the leg of the retaining device. The compression spring thereby forms a second axial flow path through the armature.

It is therefore an object of the present invention to provide a new and improved immersion motor fuel pump.

Another object of the invention is to provide a fuel pump of the type described above, in which the drive member of the motor is coupled to the driven member of the pump, such as by a face dog or core joint.

Another object of the invention is to obtain a fuel pump of the above-mentioned type, in which the wear life of the pump is increased and the noise generated thereby is reduced compared to conventional slotted and keyed couplings.

Another object of the invention is to use a face dog joint to drive a driven gerotor gear while allowing for slight end-to-end self-alignment of the armature shaft with respect to the hole in the driven gear. That's true.

Another object of the invention is to support the pump end of the armature shaft in a pushing that is resiliently supported by the pump inlet and housing.

Such resilient support allows for slight self-alignment of the armature shaft relative to the gerotor element.

Another object of the invention is to increase the thrust support between the motor and the exit plate of the bong 7-.

Another object of the present invention is to provide a submerged motor fuel pump that increases flow with less armature current and delivers that flow more smoothly and at a lower temperature than conventional submerged motor fuel pumps of comparable size and capacity. It is.

Another object of the present invention is to provide a new and improved fc for flowing fuel along axial flow passages formed between the MW magnets of the motor and open inwardly toward the rotating armature.
The goal is to obtain a new structure.

Another object of the invention is to provide a magnet spacer or magnet retaining device which opens pupil-wise inward towards the armature and serves to circumferentially separate juxtaposed axial surfaces of the motor magnets; The goal is to obtain a flow path.

Another object of the invention is to provide an inlet and a pump housing;
It is an object of the present invention to obtain a submerged motor fuel pump having a pump case that aligns the main elements of the pump, including a pump outlet plate, a motor flux ring, and an outlet housing.

Another object of the invention is the above-mentioned pump case, which also serves as an inlet fitting for the pump and is sealed to the outlet housing by a lip of the pump case which is flanged inwardly over a shoulder of the outlet housing. The goal is to get a different kind of pump case.

〔Example〕

Hereinafter, the present invention will be described in detail with reference to the drawings.

First, please refer to FIGS. 2 and 89.

The figures include an immersion system that receives a fluid, such as fuel, from a fuel source, such as a fuel tank (not shown), and supplies the pressurized fluid to a utilization device, such as an internal combustion engine (not shown). A motor gerotor pump assembly or pump 10 is shown. Immersion motor gerotor pump 10 includes a cylindrical stepped case 12 . This case 1
2 includes a pump and pump housing 14 , a gerotor pump assembly 16 , a motor flux ring 17 , and a pump outlet plate or pump port plate 180 and is sealed to the outlet housing 18 . . A motor assembly 20 connects the inlet and pump housing 14
and the protrusion housing 18.

One end of the cylindrical stepped case 12 terminates in an inwardly flanged sealing lip 22 which presses against an annular shoulder 24 extending outwardly of the outlet housing 18 to effect a seal. Toward the other end, the cylindrical stepped case 12 has an outer hole 2 that generally forms a motor chamber 28.
6, a pump bore 30 generally defining a pump chamber 34, and an inner bore 36 stepped inwardly from the outer bore 26 and pump bore 30 to generally define an inlet chamber 38.

The pump bore 30 may be stepped inwardly from the outer bore 26 at the annular shoulder 32 .

The population chamber 38 is coupled in any known manner to a fuel source (not shown), such as by known fluid couplings, pipes, filters (not shown), or the like.

The inlet and pump housing 14, made of a single layer die-cast zinc construction, has a cylindrical outer circumferential wall 4o. This cylindrical outer peripheral wall 40 is connected to the pump chamber 34 of the cylindrical stepped case 12.
into the pump hole. Inlet and pump housing 14 terminate within a cylindrical hub 42 . The cylindrical hub 42 connects the inlet hole 36 and the inlet chamber 38 of the pump case 12.
It also has a stepped hole 44 extending into it and configured as will be described in more detail below. The cylindrical outer peripheral wall 45 of the cylindrical hub 42 is spaced apart from the surrounding annular spring washer 48 in an annular space 46 . An inner diameter portion 50 of the spring washer 48 is pressed against an annular hub receiving portion 52 . The annular hub receiving portion 52 extends inward from the inside of the cylindrical stepped pump case 12 .

The annular spring washer 48 also has an outer diameter 54 . This outer diameter portion 54 is connected to the inlet and the inlet side 5 of the pump housing 14.
It is captured axially and axially in a spherical end 56 formed at 8, just inside the cylindrical outer peripheral wall 40.

Motor assembly 20 has an armature shaft 60.

The armature shaft 60 has an armature shaft inlet end 62 and an armature shaft outlet end 64. Each shaft end 62 , 64 is rotatably supported in a respective cylindrical bushing or bearing 66 , 68 in a loose fit and bearing 66 .
68 are resiliently connected to an O-ring 70 fitted in a hole 74 in the inlet and pump housing 14 and an O-ring 72 fitted in a hole 16 in the outlet fitting 18, respectively. is supported. Cylindrical bushing 66
is lubricated and cooled by the fuel in the inlet chamber 38 , while the cylindrical bushing 68 is lubricated by the fuel passed through the axial slots 15 spaced around the bore 74 . Ru. The armature shaft 60 is located generally along the central flow axis within the immersion motor gerotor pump assembly 10 and is attached to a thrust runner 184 that is part of the pump outlet or boat plate 180 with magnets 240 . .242 and the armature stack by the thrust washer 182 pressed against it by the magnetic attraction force between the armature stack and the armature stack.
located along the central flow axis. The tubular bushing 66 at the inlet is positioned with a shoulder 80 extending outwardly therefrom and an annular shoulder 82 extending inwardly from the tubular hub 42 to capture the O-ring 70 therebetween.

Electric motor assembly 20 rotating within motor chamber 28 is
Includes armature 84. In this case, the machine root 4 includes a plurality of t root windings 86. The armature winding 86 is wound within the sieves of a plurality of grooved armature laminated plates (not shown) that are press-fit into the knurled portions (not shown) of the armature strip 60. ing. The respective first of each armature winding 86
and the second end are terminated in a known manner in a commutator 88. The commutator 88 is contacted by a pair of brushes 90, 92 that face each other in the diametrical direction of the commutator. Those brushes 90.92 are connected to the tip-shaped terminals 91.
92, respectively. Brush 90.92 is the first
The brush is pressed against the commutator 8B along the brush position axis 94 by a spring 96 and a second brush spring 98.

From the outside of both ends of the armature laminate, a first end fiber 100 and a second end fiber 102 are connected to the armature shaft 6.
It is press-fitted into the part where the 0 knurling is carved. Each end fiber has eight fingers 104. The fingers 104 extend radially outwardly from a fibrous central tubular hub 106 at equal angular intervals. The distal end of each finger is provided with a tab 108 that extends axially inwardly to separate the finger from the armature laminates. The axially outer outer surface of each finger 104 is smooth so that the finger contacts and supports the end loops of the armature winding 86 without stripping the insulation sheathing of the end loops. It is bent to Fibrous central cylindrical hub 106 of end fiber 102
An annular thrust shoulder 110 extends radially inward from l1 to form a pair of drive tangs or dogs 112, 114.
It terminates in the direction of the aI line. The dogs 112-114 are in the form of diametrically opposed arcuate sections extending axially into the inlet and pump housing 14, as best shown in FIG.

As best seen in FIGS. 2, 3, and 9, the inlet and housing 14 have a counterbore 116 that is open toward the armature 84. As best seen in FIGS. The edge portion 116 forms a vomit side 118, through which a central hole 120 passes. The end comb 116, the gerotor cavity 118, and the center hole 120 are coaxially arranged about an eccentric axis 122 (FIGS. 3 and 9). The eccentric axis 122 has a predetermined radial offset 124 from the central flow axis 78 along a first radial direction generally perpendicular to the brush displacement axis 94 . As best shown in FIGS. 2, 4, and 9, the end gouge 116
On the bottom surface 130, there are an oval groove 126 and an oval hole 1
28 are provided coaxially around the center hole 120.

As best shown in FIG. 4, an axially extending oblong inlet recess 132 is provided in the inlet and inlet side 58 of the pump housing 14. The first on the inlet side 58
The oval recess 132 is formed on the bottom surface 130 of the end comb portion 116.
an oblong hole 128 provided in the inlet and a second oblong recess 1 on the inlet side 58 of the inlet 140
It leads to 36. The second oval shape (the recess 136 is the bottom surface 1)
The c1 first oblong indentation 132 and the second oblong indentation 136 that communicate throughout the oblong hole 128 of 30 cooperate to provide unpressurized fluid or fuel to the gerotor cavity 118 to The fuel is pumped into the rotor bong assembly 16 and compressed by each pump.

Inside the grotor cavity 118 of the gerotor pump assembly 16 are an inner pump gear 142 and an outer pump gear 144.
(Figure 3). Inner pump gear 142 has inner pump teeth 154 and outer pump gear 144 has outer pump teeth 156. A tooth gap 158 is provided between the inner pump teeth 154 and the outer pump teeth 1560.
A pump interdental PA 160 is provided therebetween. Inner pump gear #154 of inner pump gear 142 is configured to engage outer pump teeth 156 of outer pump gear 144 to seal the pump tooth gap while delivering fuel. Outer pump teeth 156 of outer pump gear 144 are configured to mesh with inner pump teeth 154 of inner pump gear 142 to seal pump tooth gap 15B. lA11
Il pump gear 144 has a cylindrical outer wall 162.

The cylindrical outer wall 162 is received in a loose fit within the counterbore 116 of the Gerotor 9 cavity 118 and is positioned within the counterbore 116 . Inner pump gear 142
A center hole 164 passes through the center hole 164 . As seen in FIGS. 2 and 5, the central bore 164 has an opening 166 that tapers toward the inlet and the bottom surface 13G of the counterbore 116 of the pump housing 14. As shown in FIGS. The end 62 of the armature slot 60 closer to the inner pump gear 1420 control large 164
However, by slightly pivoting about the other end 64 with respect to the control hole 164, the armature narrow 600 Å mouth end 64 can center itself within the hole 14 of the cylindrical hub 42 by the O-ring 10. As such, the inner diameter of the control hole 164 of the inner pump gear 142 is such that the armature @116G threaded therein is
outside diameter) slightly (for example, about 0.025 crn (0,
001 inch) and the axial length of the control hole 164 is relatively short (e.g., about 0.127 crn (0.005 inch)) than the inner diameter of the control hole 164.
) is selected to be. By enabling self-centering in this manner, it is possible to reduce the angle formed by the armature shaft 6o with respect to the central flow axis T8, which increases as manufacturing errors and assembly errors increase.

As can be clearly seen from FIGS. 3 and 9A, although the armature shaft 60 can be self-centered relative to the inner pump gear 142, the armature shaft 6o still
42. Inner pump gear 142 has a pair of driven dogs 172,174. The driven dogs extend radially inwardly from the inner pump gear 142 into the drive coupling cavity 110. To form the drive joint 116, as best shown in FIGS. 3 and 9A,
The included angle of each drive dog 112, 114 is about 118 degrees, and the included angle of driven dogs 172, 174 is about 58 degrees. Besides, those dogs 112, 114
, 172, 174 have a full circumferential gap of approximately 8 degrees. Such a clearance provides sufficient circumferential clearance to facilitate assembly of the drive coupling, but the inner pump gear 14
It also provides a reliable axial position offset to allow for end-to-end self-centering of the armature narrow 6° relative to 2.

Gerotabonds assembly 16 includes annular pump outlet plate 1
80 and Teflon loaded Ultem (
It is completed with a thrust washer 182 made by Ultem. Pump outlet plate 180 has an annular thrust surface 184
and a through hole 188. The outlet side 186 of the thrust surface 184 is kneaded down. The diameter of the hole 188 is sufficient to allow the drive dogs 112, 114 of the fibrous central tubular hub 106 to pass freely therethrough with a suitable clearance (eg, approximately 0.125 crn (0.005 inch)). It's the size. The fs-shaped pump outlet plate 180 has a cylindrical outer wall 19Q and a radial groove 192 extending inwardly therefrom. The cylindrical outer wall 190 is a cylindrical stepped case 12.
is received in the outer bore 26 of the motor and pressed against the surface of the annular shoulder 32 for axial and axial positioning relative to the motor flux ring 17. Thrust washer 182
is the annular thrust shoulder 11 of the fibrous central cylindrical hub 106.
0, the acknowledgment thrust surface 184 of the pump outlet plate 180
be forced to. The thrust washer 182 has a pair of arcuate dogs 193a, '19 facing each other in the diametrical direction.
3b. The arcuate dogs extend radially inwardly to the dogs 112 , 114 of the fibrous central tubular hub 106 .
and are driven by their dogs.

On the axial side facing inner pump gear 142 and outer pump gear 144, pump outlet plate 180 also has an oblong indentation 196 and an outlet hole 198. those hollows 196
and the shape and location of the outlet hole 198 are similar to the bottom surface 1 of the corner 9 portion 116 of the gerotor cavity 118 of the inlet end pump housing 14.
Oval hole 126 and oval hole 1 provided in 30
28 in shape and position, respectively.

To obtain proper priming characteristics of the pump and other desirable pump characteristics, the oblong hole 128 and the oblong recess 196 are each provided with an appropriate slot (200).
202 through hole 120°188 (second
Figure 9). Additionally, the annular pump outlet plate 180 includes an oblong outlet hole 1 to provide an outlet port in the gerotor cavity 118 suitable for fully pressurizing the fuel to a certain pressure.
98 is formed. The location and shape of the exit hole 198 correspond to the location and shape of the oblong groove 12B, respectively. Pump outlet plate 18 for inlet and pump housing 14
A pair of locating pins 204, 206 are secured to the pump housing 14 to properly position G in the circumferential direction. The locating pins extend axially from the annular radial surface 208 to the pump outlet plate 180.
into suitable holes 205, 207 provided in the annular radial surface 209 of.

Pressurized fuel exiting the oblong outlet hole 198 of the pump outlet plate 180 is directed to the tunnel and magnet retainer 210 (FIG. 7).
9) and are protected from the fluid action generated by the armature 84. The tunnel die and magnet retaining device 210 constitutes an M1 flow path 211 that is shielded from the fluid pull and pull effects generated by the armature.

The flow passage 211 extends between the pump outlet plate 180 and the annular shoulder 24 of the outlet housing 18 over substantially the entire axial length of the motor chamber 28 . The overall U-shaped tunnel and magnet holding device [210 is a pair of legs 21
4 and 216, and a central connecting portion 212 that connects the legs. To match the circular contour of the outer circumferential surface of the armature 84, the central joint 212 is convex when viewed from a point outside the pump, and has a pair of legs 214;
216 extends radially outwardly from central coupling portion 212 to contact inner circumferential surface 218 of cylindrical motor flux ring 17 . Flux ring 17 extends substantially axially between pump outlet plate 180 and an outwardly extending annular shoulder 24 of outlet housing 18 .

Allowing pressurized fuel to flow from the oblong exit hole 198 into the tunnel and magnet retainer '210 with little obstruction, yet at the desired circumferential location of the tunnel and magnet retainer frt210. Two axially extending protrusions 224, 226 are provided at the inlet end 222 of the tunnel and magnet retaining device 210 to allow the tunnel and magnet retaining device 210 to take the same position. The protrusions are radially spaced to form a fluid inlet 228 therebetween. The axial protrusion 224 has an abutting end 230
Terminates with. Its abutting end 230 directly contacts the annular radial surface 209 of the pump outlet plate 180 . The m-line projection 226 terminates in a stepped tab 232 . The abutting end 232a of the stepped tab 232 contacts the annular radial surface 209. Stepped tab 232 is bin 2
It also has 32b. The bin 232b extends into the outlet side of the hole 207 provided to properly orient the pump outlet plate 180 relative to the inlet and pump housing 14, as previously described.

Legs 214° 21 of tunnel and magnet holding device 210
6 cooperates with a pair of tabs 234 , 236 extending circumferentially outwardly from axial projections 224 , 226 , respectively, to position a pair of crescent-shaped motor magnets 240 , 242 circumferentially and outwardly relative to armature 84 . Proper axial position. As best seen in FIGS. 7, 8, and 9, each crescent-shaped motor magnet 240° 242 has first and second axial surfaces 240a that are parallel along the axial direction.
, 240b and 242a, 242b,
On the other hand, the inlet end and outlet end of each crescent-shaped motor magnet 240, 242 are limited by respective end faces 24θC 2242c and 240d, 242d.

During assembly, the pin portion 232b of the tunnel and magnet holding device 210 is inserted into the locating hole 207 of the pump outlet plate 180.
Attach the tunnel and magnet retaining device 210 first by inserting it into the hole. Thereafter, each axial surface 24 of the crescent-shaped motor magnets 240 , 242
Crescent-shaped motor magnet 240 is configured such that 0a and 242a contact legs 214 and 216, respectively, and end faces 240c and 242c contact tabs 234 and 236, respectively.
, 242 is inserted. Crescent-shaped motor magnet 240, 2
42 are arranged with a suitable spacing between them and the pump outlet plate 180 to provide a second axial passageway 211a therebetween.
A V-shaped compression spring 246 is inserted between the holes 246 and 24b to force the axial surfaces 240a and 242a circumferentially into contact with the legs 214 and 216 of the tunnel and magnet retainer 210.

Finally, the outlet housing 1 is placed inside the cylindrical stepped case 12.
Insert 8. The circumferential orientation of the outlet housing 18 is determined by the arcuate tab 248 extending between the axial surfaces 240b and 242b of the crescent-shaped motor magnet 240, relative to the tunnel and magnet retaining device 210 ( Figure 8). Besides, pump outlet boat 252
through the outlet housing 18 and the center of the tunnel and magnet retainer 210 and the outlet hole 1 of the pump outlet plate 180.
98 centers along the same plane.

Due to the proper circumferential orientation of the outlet housing 18 relative to the tunnel and magnet retainer 210 described above, pressurized fuel flows from the outlet hole 198 through the first flow passage 211 into the outlet housing 18. This allows smooth flow to the pump outlet boat 252.

Experiments conducted under standard conditions have shown that the device described above significantly improves pump performance. Compared to conventional immersion pumps of similar size and capacity, the nine immersion motor pump assembly described above is capable of delivering significantly increased flow rates of fuel at desired pressures with less armature current. For example, in a typical application to a conventional passenger car internal combustion engine, the flow rate increases uniformly by at least about 3 gallons per hour, and the corresponding armature current increases by at least 12 gallons per hour. %Diminished.

Some of this improvement is due solely to the provision of an axial flow path, such as a magnet retainer 210a of the type shown in FIG. 9B. Such a magnet holding device includes a central coupling portion 212a that contacts the magnetic flux ring 17, and an armature 8. ．． 4. It has a pair of legs 214a and 216a that open radially inward toward. However, due to the magnet holding device, the aftereffects of the armature are
11b causing a radially directed fluid twist. However, due to the turbulent flow, the axial passage 211b
The effective cross-sectional area of becomes υ smaller than the actual cross-sectional area.

In order to avoid such fluid twisting and turbulence and to significantly increase the effective cross-sectional area, the central joint 22 of the tunnel and magnet retainer 210 shields the flow of fuel flowing from the armature aftermath flow. The preferred embodiment tunnel and retention device 210 is provided to do so. If further improvements are desired to avoid flow direction-induced fluid tortuosity within the flow passage 211 due to the flow restriction imposed by the circumferential width of the flow passage 211, the flow The passageway 211 is further divided into narrow passageways consisting of a plurality of tubes or slots. Multi-layer flow is generated through these narrow passages, greatly increasing the effective cross-sectional area of the flow to the actual cross-sectional area of the passage.

The outlet housing 18, which is molded from a plastic such as Ultem, as best shown in FIG. The tubular outlet boat or outlet of this outlet valve 250 and 9
A fitting 252 is coupled to the internal combustion engine. , tubular outlet fitting 252 has an internal outlet passageway 251 with a slotted seal 253 fitted into an outlet hole 254 to accommodate the ball valve 255 of the one-way check valve 256 therein. Outlet housing 18 has an annular receptacle 257 .

This annular receptacle cooperates with ball valve 255 to form a one-way check valve 256 that prevents backflow from the internal combustion engine to the pump. It terminates in four tapered branches 258 forming slots 259 to allow normal flow from the pump 10 to the tubular outlet. Tapered branch part 2
58 normally prevents outward movement of ball valve 255 and allows fuel to flow through slot 259. The angle formed by the tapered branch portion 258 is such that the angle formed by the tapered branch portion 258 allows the ball valve 2 to resist vibrations of the ball that occur at certain flow rates.
It's like receiving a 55.

Another feature of the submerged motor pump assembly of the present invention is a steam exhaust valve 260 located in the outlet housing 18 (FIGS. 6 and 6A). The steam exhaust valve 260 is the outlet valve 2
50 and includes a ball 262 contained within a valve hole 264 that is disposed diametrically opposite to the tubular outlet and fitting 266 . A discharge passage 268 passes through the discharge port and the fastening fitting 266. Annular hub 21 of steam exhaust valve 260
0, the annular receiver of the outlet housing 18 is received by the surface 212. A helical spring 274 attaches the ball 262 to the shoulder 27 surrounding the annular internal hub 278 of the tubular outlet fitting 266.
6 and push toward an incomplete seal (FIG. 6A) in the form of a square receptacle 280 at the end of the punch hole 282 formed in the outlet housing 18. The ball 262 has four points 28 in the square receiving part 280.
Contact only at 4a, 284b, 284c, 284d. For this purpose, four side roads 286a, 28
6b, 286c, 286d are formed. These bypasses allow the vapor pressure generated within the gerotor pump assembly 1'6 to escape, particularly during self-priming of the pump, until the fluid reaches the outlet side of the pump element and the vent hole 282. . Thereafter, when the fluid pressure on the ball 263 becomes greater than the force exerted on the ball 262 by the helical spring 214, the tubular outlet and the fastening fitting 266
The exhaust passageway 268 is closed by an annular internal hub 278 formed at the inner end of the outlet boat 252, allowing fuel to flow through the outlet boat 252 to allow normal pumping operation. It becomes like this.

In place of the square receptacle 280 formed on the steam exhaust valve 260, any other suitable non-circular receptacle, ie, an incomplete receptacle, may be used. The incomplete receiver or valve seat also includes a partially circular valve seat, such as a circular valve seat having an axially extending slot extending therethrough.

Another use for a defective valve seat is as a deformed protrusion housing 1.
Discharge relief valve 2 molded in 9 (Fig. 10, Fig. 11)
It is a combination with 90. As can be seen from the figures, a ball 292 is inserted into a hole 294 provided in the outlet housing 19 and defining a valve chamber 295. One end of the hole 294 always communicates with a discharge relief passage 296 provided at one end of the outlet housing 19, and the other end of the hole 294 is fixed to the valve seat member 298 by, for example, ultrasonic welding.

A central passageway 300 passes through the valve seat member 298, the central passageway having a chamfer hole having a width equal to the diameter of the central passageway 300 and a length twice the diameter of the central passageway. When in contact with the valve seat member 298, the ball 292 contacts the oval valve seat 301 at two diametrically opposed points when centered; When placed at the edge of the line, it makes a semicircular line contact. In any case, between the ball 292 and the oval valve seat 301 there is a side passage that is always open, one hole 294 and the valve seat member 2.
A tubular relief valve 302, a first helical spring 304, and a second
A helical spring 306 and an O-ring 308 are provided. The first helical spring 304 has one end pressed against an existing shoulder 310 formed in the discharge relief passage 296 and the other end pressed against an annular top surface 312 formed at the top of the relief valve 302. , its annular top surface 312
6 surrounding a central exhaust passageway 314 passing through the relief valve 302.
．． The first helical spring 304 normally forces the tubular relief valve 302 against the O-ring 308 to provide a seal. The O-ring 30B is normally pressed against the annular face 316 provided around the oblong valve seat 301 of the valve seat member 302. When the relief valve 302 is pressed against the O-ring 308 and the annular receiver seals the surface 316, the valve seat member 2
The discharge relief passage 2 of the housing 19 exits from the center passage 300 of 98 through the middle 6 discharge passage 314 of the relief valve 302.
A side road leading to 96 is formed. The discharge bypass is such that the pump assembly 10 is connected to the ball 29 as will be explained later.
2, it is closed when a fluid pressure higher than the predetermined maximum discharge pressure is generated.

Tubular relief valve 302 has an externally slotted tubular portion 318. A ball 292 is attached to one end of this tubular portion.
A tubular hole 320 having a diameter larger than the outer diameter is formed, and a tubular hub receiving portion 322 extending inward from the other end is formed. The second helical spring 306 is received at one end around the tubular hub receiver 322 and at the other end by the ball 292.
The ball 292 is normally pressed against the oblong valve seat 301 by contacting the outer surface of the valve seat 301 . However, when the fluid pressure experienced by the pump 10 exceeds a predetermined maximum discharge pressure, the fluid pressure becomes stronger than the force of the second helical spring 306 applied to the ball 292, forcing the ball 292 into the annular hub receiver. 322 and forces the ball 292 against its annular hub receptacle 322 when the pump pressure exceeds a predetermined maximum discharge pressure. At pump pressures intermediate between the maximum discharge pressure and the predetermined relief pressure, the ball 292 Fi closes the fluid passage between the center passage 300 and the discharge relief passage 296.

The axial outer wall 324 of the relief valve 302 includes six ridges 326a, 326a, 326a, 326a, 326a, 326a, 324a, 324a, 326a, 326a, ?
326b, 326c, 326d, 326e
, 326f are provided. The ridges are equally spaced around the outer wall 324 of the tubular portion 318 and extend radially outwardly. Those raised parts 326a-3
26f is the hole 29 when guiding the relief valve 302.
Position it in the center relative to 4. Each axial ridge 32
6a-326f are spacer tabs 328 disposed circumferentially on and axially projecting from the tubular top surface 312;
8 to 328f, respectively. A central exhaust passageway 314 extends through the relief valve 302 . Tabs 328a-328
f prevents the portion of the relief valve 302 other than the tabs 328a to 328f from moving axially away from the nut top surface 330 even if it contacts the annular stop surface 330 that is depressed around the discharge relief passage 296 of the outlet housing 19. It's supposed to separate them. Raised portions 326a-326f and tabs 328a-
328f form passageways or slots 332a through 332f arranged at equal angular intervals around the axial outer wall 324 of the relief valve 302. Slots) 332a to 332f are combined with the discharge relief passage 296 and are connected to the hole 294 and the axial outer wall 3 of the relief valve 302.
The entire space between 24 is always in communication with the exhaust relief passageway 296 3, but that space is not in communication with the central passageway 300 until the pump develops fluid pressure on the relief pressure plate. Since the fluid pressure on the relief pressure plate is greater than the force of the first helical spring 304 applied to the O-ring 308, the relief valve 302 will cause the annular receiver to move away from the surface 316 and toward the annular stop surface 330. Moved. In turn, the high fluid pressure pushes the relief valve away from the O-ring 308, causing the annular receiver to separate from the surface 316 and slot out of the central passageway 300 between the hole 294 and the axial outer wall 324 of the relief valve 302. 332a-332f are opened to allow exhaust relief passage 296 to flow through slots 332a-332f.

A further feature of the pump 10 shown in FIGS. 10 and 10A is additional tubular bushings 340, 340a.

The outer axial walls of these bushings are convex in the form of an outwardly raised bowl or crown 342;
Its crowned portion 342 contacts the inner surface of the hole 344 in the outlet-housing 19 to allow slight self-extraction between the ends of the armature shaft 60. To limit rotation of the tubular bushing within the bore 344, an anti-rotation mechanism is provided in the form of a slot key mechanism 348. The slot 348a in the tubular bushing 34G is somewhat wider in the circular direction and somewhat deeper in the radial direction than the key 348b.

Another feature of the immersion motor pump 10 is to provide another outlet housing 19 with cooling and lubricating the portion of the tubular bushing 340 that is included between the contact point of the ridge 346 and hole 344 and the roof 360 of the outlet housing. using conventional construction combined with additional passages for the purpose. As can be seen from the views of the outlet housing 19 shown in FIGS. Cylindrical outer peripheral surface 89, hole 344, and brush 90
．． A pair of brush support parts 35'6 each supporting 92
, 358.

As best shown in FIG. 12, the raised cap portion 352 supports the outlet valve 250 and discharge relief valve 290 hose fitting 7; A generally flat roof 360 supporting the relief valve 290 hose fitting and a pair of side walls 362, 36.
4 and a pair of curved end walls 366°368.

Flow network 354 has the general shape of a Roman numeral X when viewed in the lateral student plane of FIG.

More specifically, the flow network 354 has four branches 370, 372, 374, each shaped like a dog's paw.
It has 376. Each branch communicates with the axial length of the bore 344 and an annular recess 378 surrounding a stop hub 380 extending from the roof 360 into the bore 344 . Each branch 370-376 extends axially along the hole 344 to the inner surface 361 of the roof 360, and includes a sidewall branch 370a,
372a r 374a, 376a included.

Each sidewall branch is parallel to one of the sidewalls 362, 364, and sidewall branches 370a and 372a are connected to the exhaust relief valve 290.
straddles the entire side wall branch part 374a, 3γ6a
spans exit boat 250 in its entirety. Each branch 37
0°372, 374, 376 are the radial branch parts 3
70b, 372b.

Also includes 374b and 3γ6b. Each radial branch terminates in a respective sidewall branch. Its sidewall branches include respective radial slots 370c + 372
c.

374c and 3γ6c are the hole wall 3 forming the hole 344
82 in the circumferential direction.

The brush support portion 35 is an arcuate ridged crown element or wall element 356a facing the radial circular side.
58a. Wall element 356a is sandwiched between a pair of radially ridged side walls 356b, 356c, and wall element 358
a is sandwiched between a pair of radially ridged side walls 358b and 358c.

Each radial ridge sidewall 356b, 356c, 35
8b, 358c are radially spaced apart at an included angle of approximately 90 degrees and each arcuate ridge wall element 356a, 3
58a and extends radially to the arcuate ridge wall depression 384.

The kneading depth of the kneading portion 384 corresponds to the width of the commutator 88 in the axial direction. Arcuate ridge wall elements 356a and 3
The diameter of 58a is slightly larger than the diameter of commutator 88,
A gap is provided between the brushes and commutator to allow for proper interaction between the two. The hole 344 starts from the depth of the arcuate ridge swell 384 and extends axially to the inner surface 361 of the roof 360 . Since the holes 344 begin below the brush supports 356 and 358, there is a portion of an approximately 90 degree arc between the opposing radial ridge sidewalls of the brush supports 356 and 358. In other words, there is a circumferential gap of approximately 90 degrees extending the axial length of commutator 88 between radial ridge sidewalls 356b and 368b, and a similar gap exists between radial ridge sidewalls 356c and 358c. Extends circumferentially between.

'llr, when the machine 84 is supplied with a root flow and rotates counterclockwise as seen in FIG. 13, the cylindrical outer circumferential surface 89 of the commutator 88 viscously draws the fluid. The fluid being pulled is caused by the rotation of the commutator, and the radial ridge side wall 356c,
358b, each having a radial slot 376c.
, 372c and slot 374c.
, 370c, each of the following radial ridge sidewalls 358
c, sent to 356b. Accordingly, diametrically opposed radial ridge sidewalls 356c, 358b
The fluid that is forced into the groove 9 is also given a high velocity, as is the fluid that is collected against the diametrically opposed radial ridge sidewalls 356b, 358c. Due to this speed difference,
Because the fluid in radial slots 370c, 374c is moved more slowly, radial slot 372c
.

376c. Similar pressure differentials can be provided by other structures such as vanes or other flow-resisting features. The funnel sidewall in the embodiment described here serves the dual function of supporting the brush and providing the necessary pressure differential.

In any case, the pressure difference generated by the drawstring of the outer circumferential surface 89 of the commutator 88 exerted on the fluid at the radial ridge sidewalls shown is the same as that of the radial branch 3
70b, 374b. Such pumping action occurs axially outward toward the inner surface 361 of the roof and then into the annular groove 378.
and then act radially inwardly until the tubular bushing 34
0 and then the tubular recess 37
8 and finally back to the facing radial branches 372b, 376b. In other words, the cylindrical outer circumferential surface 89 of the commutator, the brush supports 356° 358, and the flow network 354
forming two parallel pump chambers or pump circuits separated at 8 but joined at a tubular conduit 378. The pressure difference generated due to the velocity difference in the radial ridge sidewalls shown therein results in two incoming fluid streams and two outgoing fluid streams. The two fluid streams are combined into tubular bushing 340 and bore 34.
4. Cool and lubricate.

It has been found that with such cooling and lubrication, the life of the upper tubular bushing 340 is significantly longer than that of a similar type of bearing without such cooling and lubrication. Historically, acceptable lubrication can be achieved by providing a single circuit leading to the annular groove 378 leading to the tubular bushing 340 above the point where the crowned portion 342 contacts the bore 344. can. The lubrication performed by a double parallel circuit has poor performance.

Furthermore, if by chance a sufficiently large pressure difference occurs between the inlet and outlet of the annular hole due to the internal structure without using a separate pressure-generating structure, such a single circuit can generate a small pressure difference. A strong fluid flow may be obtained.

[Brief explanation of drawings]

1 is an end view of one embodiment of an immersion motor gerotor fuel pump having certain features obtained in accordance with the present invention, and FIG. 2 is an axial cross-section of the gerotor fuel pump taken along line 2--2 of FIG. Figure 3 is a radial cross-sectional view of the gerotor fuel pump along line 3-3 in Figure 2, and Figure 4 is a radial cross-sectional view taken along line 3-3 in Figure 2.
Radial cross-sectional view of the gerotor fuel pump along line No. 5
Figure 6 is an enlarged exaggerated view of the armature shaft and Grotapons gear portion; Figure 6 is an illustration of the outlet housing having the outlet check valve and discharge valve of the Gerota fuel pump of Figure 1; 6-6 of Figure 1;
6A is a cross-sectional view of the incomplete valve seat and ball valve of the discharge valve along line 6A-6A of FIG. 6; FIG. 87 is a cross-sectional view of the incomplete valve seat and ball valve of FIG. Cross-sectional view of the gerota fuel pump,
Figure 9 is a schematic plan view of a portion of Figure 2 showing the orientation of the outlet housing through the use of a rationing tab located between two motor magnets; Figure 9 is shown in Figures M1 to $B. Figure 9A is a perspective view of the armature shaft, side gerotor pump gear and joint structure shown in Figures 1 to 9, and Figure 9B is the retaining device shown in Figure 7 and M9. FIG. 10 is a partial cross-section of a portion of another outlet housing showing the discharge valve and the bushing rotatably supporting the end of the armature shaft; FIG. 41 is a perspective view of a portion of an alternative embodiment of the support bushing and outlet housing of FIG. 10 showing the slotted key ms for limiting circumferential rotation of the bushing; A perspective view of the relief valve of the discharge valve shown in FIG.
12 is a top view showing another embodiment of the outlet housing shown in FIG. 10, FIG. 13 is a bottom view showing the internal structure of the outlet housing shown in FIG.
10, 12 and 13 along the line 4-14; FIG. 15 is a cross-sectional view taken along the line 15-15 of FIG. 12; , 1st
2, 13 and 14, and FIG. 16 is an exploded perspective view of a portion of another outlet housing assembly shown with a portion cut away. 10... Pump, 12... Cylindrical stepped case,
14・Fist Φ・Enter I:I Fu・Yo and pump housing, 16
・Exposure...Gerotor pump assembly, 1T...Motor magnetic flux ring, 18.19...φ・Outlet housing, 2
0...P-motor assembly, 28...Motor room,
30... Bon 7″ hole, 34... Pump chamber, 36
... Inner hole, 38 ... Inlet chamber, 42 ... Cylindrical hub, 44 ... Stepped hole, 46 ... Annular space, 48 ... Annular spring washer, 60... Armature shaft, 66.68... Cylindrical bushing, 10°7
2... O-ring, 18... Center flow axis, 84
...vt machine root 86...armature winding, 88, music...commutator, 90.92...brush, 94...
Push displacement axis! 96, 98...Brush spring,
100, 102...end fiber, 116...φ
・Edge part, 118・War・Gerota cavity, 120・・
・-Center hole, 122...Center axis, 126, 13
2 , 136... Oval neck, 128...
Oval hole, 142...Inner pump gear, 144...
...Outer pump gear, 176...Drive wJ joint, 1
98...Exit hole, 210, 210a...Tunnel and magnet holding device, 211...Dialogue passage,
240, 242...φ・Crescent motor magnet, 246
... V-shaped compression spring, 250 ... Outlet valve, 252
... Pump outlet boat, 256 ... One-way check valve, 260 ... Steam discharge valve, 290 ... Discharge relief valve, 295 ... Valve chamber, 296 ... Discharge relief passage, 302... relief valve, 308... 0 ring, 340, 340a... tubular bushing, 348...
fist/φ slot) - key mechanism, 354...9 flow circuit network, 356 i 358... brush support section, 360...
...Roof, 370°372, 374, 376...
...branching of the flow circuit network. Patent applicant Facet Enterprises, Inc. Agent Makitana Yamakawa (and 2 others) Tou

Claims (1)

Claims: (1) a pump case having one end, an opposite end, an X-through flow axis, and an inlet end hole at said one end communicating with a fuel source; adjacent said inlet end hole; a motor chamber provided in the other 4i section of the pump case; a pump chamber provided in the same portion of the motor chamber and the inlet chamber; a pump chamber provided in the other end of the pump case to accommodate the pump; a first means for sealing the case; a moat-like hub projecting into the inlet chamber and further spaced a distance eccentrically from and parallel to the flow axis; a gerotor cavity disposed about a gerotor axis, the inlet housing means being disposed within the pump chamber; and a second sealing means coupled to the first sealing means communicating with the internal combustion engine. an outlet housing means having a pump outlet means; a first end rotatably supported in said inlet housing means and a second end rotatably supported in said outlet housing means; an armature shaft having an armature shaft and further having a drive hub means having a first tang means extending in a first radial direction relative to the armature shaft; Pump gear 1. gerotor pump means having an outer pump wheel and a second core means disposed in one of the inner and outer pump gears and disposed within the gerotor cavity; Child means further extend in a second radial direction radially offset from the radial direction of said M1, and said fuel pump delivers fuel from said fuel source to said inlet chamber and from there to said gerotor. means and said motor means drivingly coupled to said first core means for entering said outlet housing means substantially along said flow axis and into said internal combustion engine. An immersion motor gerotor fuel pump for delivering fuel from a fuel source to an internal combustion engine. (2. The submerged motor gerotor fuel pump according to claim 1, wherein one of the inner pump gear and the outer pump gear has a coupling cavity, and the second core means is arranged in the coupling cavity. said drive) extending radially into said first core means and said drive means extending axially into said coupling cavity such that said first core means couples to said second core means; Motor gerota fuel pump. (3) An immersion motor gerotor fuel pump according to claim 1, wherein the first end and the second end of the armature shaft are connected to the inlet ronrowing means and the outlet housing means. first bearing means and second bearing means each supporting the armature shaft in an axial direction offset from the flow axis; 1. An immersion motor gerotor fuel pump, characterized in that it comprises resilient mounting means adapted to be aligned with the immersion motor gerotor fuel pump. (4) The immersion motor gerotor fuel pump of claim 3, wherein the first end of the armature shaft has an outer shaft diameter and passes through a hole in the inner pump gear. the diameter and length of the hole in the inner pump gear are such that the armature shaft can pivot within a predetermined range of angles with respect to the flow axis, and A submerged motor gerotor fuel pump characterized in that resilient mounting means and said predetermined angular range are combined to allow said armature shaft to automatically align with said flow axis. (5) A submerged motor gerotor fuel pump according to claim 1, wherein the motor means includes an inner axial surface and an outer axial surface extending around the armature means in a direction along the flow axis. and first and second magnet means respectively comprising a first side surface and a second side surface extending in a direction along the flow axis, and a first end surface and a second end surface. the second side on the first side
located between said first magnet means and said second magnet means to circumferentially separate a side surface of said second magnet means from said first side surface and said second side surface of said second magnet means. and magnet spacing means. (6) The immersion motor gerotor fuel pump according to claim 5, wherein the magnet spacing means is arranged such that one of the first side surface and the second side surface of the first magnet means is separated from one of the first side and the second side of the second magnet means, between the gerotor pump means and the outlet housing means, and between the first magnet means and the second side. retaining means for forming an axial flow passageway generally along said flow axis between the magnet means so that said axial 1AitL passageway improves shipping efficiency by directing fuel around said armature means; An immersion motor gerotor fuel pump characterized by improved pumping performance. (7)4! The submerged motor gerotor fuel bong according to claim 6, wherein the magnet spacing means
The other of the first side surface and the second side surface of the magnet means is connected to the first side surface and the second side surface of the second magnet means.
a second l1IlIl line extending along the flow axis between the first magnet means and the second magnet means offset circumferentially from the other of the side surfaces of the magnet means; An immersion motor gerotor fuel pump characterized in that it comprises spring means. (8) having an inlet end and an outlet end in communication with the fuel source, and further provided coaxially with the flow line between the ends, including a chamber and a pump chamber; 1. each forming an entrance chamber. a pump case having second and third holes; a pump cavity within said pump chamber; and further having a hub projecting into said population chamber and inlet housing means received within said pump chamber. and; an outlet housing means having an outlet means communicated with the internal combustion engine; having a port plate through which an outlet port passes, for directing pressurized fuel from the inlet chamber through the outlet boat and into the motor chamber. operative pump means; an armature shaft having a first end rotatably supported in said inlet housing means and a second end rotatably supported in said outlet housing means; and a first radial direction extending in a first radial direction relative to the armature axis.
a motor means comprising an armature means having a drive hub means having a core means of; and the motor means of said flow rl! first and second surfaces each having an inner surface and an outer surface extending along line III, first and second side surfaces extending along the flow axis, and a first end surface and a second end surface, respectively; magnet means and circumferentially separating said first side and said second side of said first magnet means from said fourth side and said second side of said second magnet means; magnet spacing means positioned between said first magnet means and said second magnet means for the purpose of transporting fuel from a fuel source to an internal combustion engine. (9) Permissible range of claim 8. The immersion motor fuel pump according to claim 8, wherein the magnet spacing means includes one of the first side surface and the second side surface of the first magnet means. separated from one of the first side surface and the second side surface of the second magnet means, between the pump case and the armature means, and between the first magnet means and the second side surface. A submerged motor fuel pump comprising retaining means defining a axial flow passage extending axially along said flow axis between the magnet means. αα The immersion motor fuel pump according to claim 8, wherein the magnet spacing means is arranged such that the other of the first side surface and the second side surface of the first magnet means is connected to the second side surface. along the flow axis between the first magnet means and the second magnet means, offset circumferentially from the other of the first side and the second side of the magnet means. A submerged motor fuel pump comprising spring means defining an axially extending second axial flow passage.