JPH09133058A - In-tank installation type fuel pump and reservoir - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electric fuel pump and a reservoir, which can supply the fuel in all liquid-level condition of a fuel tank and in which a steam discharging device can be operated so as to maintain the appropriate quantity of fuel. SOLUTION: A main filter 18 for feeding the fuel to an inlet 16 of a fuel pump 14 is provided, and the main filter 18 is housed adjacent to a bottom of a fuel tank 12, and a reservoir cylinder 26, which is arranged in the vertical direction, a flow control outlet means of an outlet part, which is provided directly adjacent to a lower end of the reservoir cylinder 26 so as to communicate the lower end thereof with inside of the main filter 18 in relation to a fuel flow from the reservoir cylinder to the pump through the inside of the main filter, and a fuel pump are provided outside of the reservoir pump 26 adjacent thereto. An inlet of the fuel pump is provided at a height as same as a lower end of the reservoir cylinder, and a bypass flow passage for connecting an outlet 20 of the pump and the reservoir cylinder to each other so as to passing a part of the fuel through the reservoir cylinder is provided, and when the supply of the fuel from the tank to the filter is interrupted, the fuel from the reservoir cylinder is flowed to the fuel pump through the flow control means and the inside of the filter.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vehicle fuel system, and more particularly to an electric fuel pump and a reservoir installed in a vehicle main fuel tank.

[0002]

2. Description of the Related Art Conventionally, a turbine vane pump positive displacement gear rotor pump is arranged in a fuel reservoir cylinder housed in a fuel tank and has been used for supplying liquid fuel to an engine of a vehicle. One preferred positive displacement gear rotor electric fuel pump is disclosed in U.S. Pat. No. 4,697,995, and one suitable turbine regenerative fuel pump is disclosed in U.S. Pat. No. 5,257,916.

[0003]

Prior to the present invention, a turbine type impeller pump arranged in a reservoir cylinder in a tank has a sufficient steam in a place where temperature conditions are bad or other steam is generated. I could not escape and could not drive normally. It has been found that the impeller pump cannot discharge steam unless the pressure difference between the pump inlet and the steam outlet exceeds about 2.5 inches of head pressure.

Positive-displacement pumps, on the other hand, have a reservoir cylinder full and when the gravitational pressure exerted on the pump inlet by fuel in the tank outside the reservoir cylinder is very low, for example, from about 6 to 10 or 12 inches. The steam can be discharged to the reserve cylinder against the fuel gravity differential pressure of the water head pressure.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a fuel supply system, method and module located in a tank which solves the above mentioned problems and, according to the present invention, can be stored at all fuel tank levels. It is possible to operate the steam venting device by using an existing positive displacement pump housed in a reservoir cylinder instead of a turbine vane fuel pump that can supply sufficient fuel and has favorable operating characteristics. Maintain a selectable amount of fuel and prevent pump depletion at bad fuel tank levels.

It is a further object of the present invention to provide a device, method and module in a fuel supply tank having the features described above, in which the fuel pump is selected from fuel in the main fuel tank and reserve fuel in the reservoir cylinder. You can pull it. The reserve fuel in the reservoir cylinder is kept in a state that it does not overflow by the bypass fuel return line under normal operating conditions, and all the advantages of the reservoir in the tank are exerted together with all the advantages of the turbine vane fuel pump. It promotes the self-vaporizing capability of the vapor venting device incorporated therein to ensure that dual filtered bypass fuel is returned to the pump inlet, rather than overflowing back into the fuel tank.

Other object features and advantages of the present invention are:
A fuel supply module for a vehicle tank having the above-mentioned characteristics is provided, in which a fuel pump is directly installed in the fuel in the vehicle fuel tank, and an associated in-tank reservoir cylinder in the fuel tank is the main fuel tank. Fuels the pump through the main fuel inlet filter when the fuel flow from the is interrupted. The fuel flowing during the interruption is double filtered. Ingress of air and fuel vapors into the pump inlet is prohibited during the interruption of fuel supply from the tank. This reservoir cylinder and pump assembly is small, sturdy, durable, reliable, relatively easy to manufacture and assemble economically, and has a long service life.

The foregoing and other objects, features, and advantages are illustrated in the Detailed Description of the Preferred and Optimum Embodiments of the Invention, the Claims, and the accompanying Drawings (in drawing dimensions unless otherwise noted). It will be revealed from.

[0009]

DETAILED DESCRIPTION OF THE INVENTION FIG. 1 illustrates a fuel pump module assembly 10 of a first embodiment of the invention, typically mounted on a fuel tank 12 of a vehicle such as an automobile, typically, A liquid hydrocarbon fuel, such as gasoline, is supplied to the vehicle engine from which the fuel is injected. The assembly includes an electric fuel pump 14, which has an inlet 16 connected to a primary or main fuel filter 18 and a bypass pressure regulator that regulates the fuel pressure delivered to the engine through conduit 24. An outlet 20 leading to a valve 22. The fuel reserve cylinder 26 has a bypass pressure adjusting valve 2 at its upper end.
The second bypass fuel outlet 28 is connected to the inside of the main fuel filter 18 through an orifice plate 30 at its lower end.

The electric fuel pump 14 has a pump assembly 32 (FIG. 1) driven by an electric motor 34 and is enclosed in a cylindrical housing 36 having a bottom inlet cap 38 and a top outlet cap 40 ( See also Figure 2.) The pump assembly 32 is a turbine pump, but could alternatively be a positive displacement pump. A suitable positive displacement gear rotor electric fuel pump is disclosed in US Pat. No. 4,697,995 and a suitable turbine regenerative fuel pump is disclosed in US Pat. No. 5,257,916, which are incorporated by reference. The electric fuel pump 14 will not be described in further detail here. However, these patents have a built-in vapor vent mechanism to allow vapor to be vented from the pump, self-pumping start, and pumping to a pressurized fuel line at hot fuel conditions. . Thus, within the electric fuel pump 14 of FIGS. 1 and 2, the rotary pump 32 of the pump assembly is shown, including a pumping chamber 33 (shown in dashed lines) and a bottom inlet cap 38 from the pumping chamber 33. Through the fuel tank 12
Has a steam discharge outlet 35 (also shown by a broken line) that leads to an outlet that directly communicates with the inside of the. The vapor vent outlet 35 is located slightly above the inlet 16, which leads directly through the main fuel filter 18 to the interior of the tank. The vapor outlet 35 is connected to the flow passages 110 and 112 shown in US Pat. No. 4,697,995, and to US Pat.
Corresponding to the 16 vapor vent holes 72, the function is similar, but improved in accordance with a further feature of the invention, the pump assembly 14 communicates externally with the fuel reserve cylinder 26 in accordance with the invention.

In normal operation, the electric fuel pump 14 is operated at a constant speed and supplies the bypass pressure adjusting valve 22 with a fuel amount larger than the maximum required amount of the engine in operation. The bypass pressure regulating valve 22 maintains the fuel supplied to the engine through its outlet 42 at a substantially constant pressure, and passes excess fuel through the bypass fuel outlet 28 into the reserve fuel reservoir of the fuel reserve cylinder 26 and into the engine. Contrary to the fuel flowing through the line 24, the bypass or discharge is performed at a variable flow rate. Typically, the fuel regulating valve comprises a diaphragm actuated flow control valve to maintain a substantially constant output pressure in response to changing engine fuel demands. Generally, the regulator valve maintains an approximately constant output pressure, such as 50 psig, and has a pressure drop capability of about 1 psi over the entire range of fuel flow to the engine from 0 to 40 gallons per hour.
Preferably, the fuel pump module assembly 10 is used in a non-return fuel system that does not have a line returning from the downstream side of the fuel injector or main fuel supply line to the fuel tank.
Bypass pressure regulating valve 22 for a fuel system without proper return is disclosed in US Pat. Nos. 5,220,941 and 5,398,
No. 655, the disclosures of which are incorporated herein by reference, and bypass pressure regulating valve 22 will not be described in further detail.

The main fuel filter 18 is a bag or an outer envelope 5.
0, the envelope 50 is formed of a flexible filter material sheet 52, such as a plastic material, is a fine mesh, the perimeter 54 of which is heat fused. The inner chamber 56 of the bag communicates with an inlet 16 of the pump through an outlet 58, which is fitted into the outlet 58 and is frictionally abutted and retained. Preferably, the outlet 58 is made of a plastic material and is secured to and sealed to the upper side wall 64 of the sheet 52 by a heat seal 62.
It has 0. A flexible corrugated stiffener plate 66, preferably a spacer that allows the passage of fuel, made from a resilient plastic material, is housed in the envelope 50 to pump the flexible bottom plate 68 of the filter member 52. It prevents the assembly from collapsing due to its weight and is also prevented from being lifted upward by the suction of the pump through the outlet 58 in the upper side wall 64, limiting the flow of fuel through the outlet to the inlet 16. Prevent

As best shown in FIG. 1, the stiffener plate 66 is preferably narrower than the main fuel filter 18 and is free within the main fuel filter 18 about the side edges of the stiffener plate 66. It allows fuel flow and is preferably made of a perforated member to allow fuel to flow through the stiffener 66. In use, the main fuel filter 18 and inlet 16 are installed in close proximity to the bottom of the fuel tank 12, preferably the bottom plate 68 of the fuel filter is installed on the bottom plate 70 of the lowest position of the fuel tank ( May be stored in the pan of the tank). To this end, the fuel pump module assembly 10 is preferably gravity biased to a suitable conventional telescopic support structure (not shown) and, optionally, biased with a coil spring and biased at the outlet hose. As a so-called bottom-down type fuel supply module, it is supported on the lower side so as to slide vertically to a flange (not shown) at the top of the conventional tank.

Preferably, the fuel reserve cylinder 26 is the tubular body 8.
It is formed from zero and is preferably formed from a plastic material that is compatible with the fuel, such as acetal. An upper side wall 64 of the filter material having a peripheral flange 82 at the lower end
Is installed on the opening 84 through and is attached and sealed by a heat seal 86. The orifice plate 30 provided on the lower side is fixed and sealed by a heat seal 88 on the filter wall adjacent to the flange, and the reservoir cylinder 80
The bottom of the reservoir so that fuel flows from the bottom of the reservoir only through the calibrated orifice 90 of the plate. The size of the orifice 90 is such that the barrel 80 is substantially completely filled with fuel being discharged from the bypass fuel outlet 28 of the bypass pressure regulating valve 22 during normal pump operation. Orifice 90 typically has a diameter in the range of about 0.1 to 0.2 inches due to normal operating pressure conditions of the fuel pump up to about 40 gallons per hour. In other words, the flow control cross section of the orifice 90 is related to the pump output and the fuel demand variable, and the fuel reserve cylinder 2
The bypass fuel input to 6 and the overflow of the fuel reservoir cylinder returning to the inlet 16 through the chamber 56 via the orifice 90 are balanced to allow fuel overflowing from the open top of the fuel reserve cylinder 26 into the main tank, If any, minimize it to get the best fuel head pressure in the reservoir barrel.

Preferably, a secondary filter 92 is provided to further filter the fuel supplied from the fuel reserve cylinder 26.
Are arranged at the bottom of the reservoir cylinder 80 and placed on the orifice 90. Preferably, the secondary filter 92 has an average pore size that the primary filter 18 has a finer mesh or pores, generally no greater than about 60 microns. Preferably, the secondary filter has an average pore size of about 30-40 microns and the main filter has a pore size of 100 microns or less, preferably about 60-70 microns. To ensure that the air or gas vapor in the returning liquid fuel does not block or restrict the flow through the orifice 90, a secondary filter 92 is disposed above, but not below, the orifice. The vapor can escape upward through the backflow fuel in the reservoir cylinder and into the head space of the tank. In use, the stiffening plate 66 ensures that the bottom plate 68 of the filter member is not pressed and collapsed against the orifice 90 and does not stop the backflow of fuel through the orifice and through the filter chamber 56 to the inlet 16. .

The cylindrical portion 94 of the housing 96 of the bypass pressure regulating valve 22 is adjacent to the upper end of the reservoir cylinder 80.
It projects through the inner hole 98 to the side wall of the reservoir cylinder 80. The peripheral annular flange 100 is integrated with the cylinder 80 and is pressed and tightly fitted to a contact pipe 102 that coaxially surrounds the inner hole 98. Preferably the O-ring 104
Seals between the housing 96 and the reservoir cylinder 80.
The upper end 106 of the reservoir barrel 80 opens into the head space of the fuel tank to prevent pressure buildup due to bypass fuel flow that would occur if the top of the reservoir barrel were sealed, and excess bypass backflow fuel was stored in the reservoir. Allow flow from top to fuel tank. A reservoir cylinder with an open top raises or separates the air or vapor in the fuel in the reservoir and separates it from the fuel in the reservoir and flows through the upper end 106 to the vapor dome in the head space of the fuel tank.

In use, the fuel pump module 10
Is located in the fuel tank, the reservoir tube 80 extends generally vertically, and the main fuel filter 18 is immediately adjacent to the bottom plate 70 of the fuel tank, preferably. It is installed on the tank bottom plate 70 as a bottom-mounted module. Inside the fuel tank, a pot-shaped container formed inside and extruded is formed at the lowest position of the tank (see FIG. 3). The module 10 with the main fuel filter 18 has a relatively short lateral dimension, which allows it to fit within the narrow shape of its pan. In normal use, the fuel tank is filled with a liquid fuel, such as gasoline, to a level above the main fuel filter 18, with the filter and inlet 16 completely submerged in the fuel.

In the normal operating state of the electric fuel pump 14,
The fuel in the fuel tank is drawn through the main fuel filter 18 to the inlet 16 of the pump, discharged from the outlet 20 of the pump to the inlet of the bypass pressure regulating valve 22, and then the outlet 42.
Fuel is delivered to the engine at a substantially constant pressure therethrough, at various flow rates, for example 50 psig, depending on the fuel demand of various engines. The bypass pressure adjusting valve 22 maintains a substantially constant output pressure by diverting a part of the fuel supplied to its inlet, and discharges the bypassed fuel to the fuel reserve cylinder 26 through the bypass outlet 44. In normal pump operation, the balance of the above-described orifice 90 and reservoir cylinder backflow fuel pressure causes the fuel in the reservoir cylinder 80 to rise to a level that is normally near or above the bypass fuel outlet 28. Under normal operating conditions, during idle or low load extension operation of the engine, the fuel level may rise to the top of the reservoir barrel 80, causing fuel to overflow the open upper end 106 of the barrel into the tank. Under certain normal conditions, some of the fuel entering the reservoir continuously flows from the bottom of the cylinder through the secondary filter 92 and orifice 90, through the internal chamber 56 of the main fuel filter 18, and out of the tank to the main filter 18. Re-enter the inlet 16 with fuel drawn through. Preferably, the level of reservoir fuel at the top of the reservoir barrel is maintained below the level that overflows the reservoir barrel, and bypass fuel already filtered by passing through the main fuel filter 18 and passing through the pump inlet is as secondary filter 92 as possible. Return to the pump inlet after being filtered again. This reduces the maximum or average flow rate of fuel drawn from the fuel tank 12 through the main fuel filter 18 and thereby reduces the amount of clogging of the main fuel filter 18 with tank contaminants. It also maximizes the amount of fuel that is double filtered and sent to the engine.

During normal operation of the vehicle when the fuel level in the tank is sufficiently low, such as during cornering, steep ups and downs, or stopping there, the fuel remaining in the tank is predominant. Displaced from the filter 18, temporarily interrupting (depleting) the fuel being pumped from the tank through the filter and through the inlet 16 of the pump. During this fuel interruption, the pump receives the reserve fuel in the reservoir cylinder 26, and in such a bad condition, the tank fuel is used in the main fuel filter 18 due to the increase in the negative pressure applied to the orifice 90 by the suction force of the pump. Reserve flow greater than possible. The reserve fuel is thus filtered by the secondary filter 92.
And orifice 90 and chamber 56 of the main fuel filter 18.
Through to the fuel pump inlet 16 which is sufficient to meet the pump and engine fuel requirements, preventing such depleted or interrupted fuel depletion. On the other hand, the fuel that exceeds the demand of the engine is continuously returned from the bypass pressure regulating valve 22 to the reservoir cylinder 80, and its backflow fuel extends the use of reserve fuel during such a bad condition.

During fuel interruption due to depletion from the tank,
The capillary action of the wet sheet of filter sheet material 52 forming the top and bottom outer walls 64, 68 causes air and fuel vapors to pass through the filter material and into the chamber 56 of the filter bag or envelope 50. Prevent flow to the pump inlet. If the fuel interruption in the tank is long enough, the reserve fuel in the fuel reserve cylinder 26 will be completely consumed, and then the filter chamber 56 itself will act as an additional reservoir or fuel reservoir for the fuel supplied to the pump. When the fuel is depleted, the stiffening plate 66 prevents the top wall 64 and the bottom plate 68 of the flexible filter material 52 from collapsing inward and the filter sheet material limiting or closing the inlet 16. It also ensures that the filter material remains wet with a small amount of the rest of the fuel and that air and fuel vapors do not enter the inlet 16 until almost all of the fuel has been consumed. The stiffening plate expands the wall of the main fuel filter 18 to normal operating conditions when the almost completely emptied fuel tank is refilled and the engine is restarted, ensuring that the fuel pump inlet 16 is not restricted. Assure.

As will be apparent from the following description and drawings, the reservoir cylinder 80, if not normally complete, is substantially filled with reserve fuel when the engine is turned off. Reserve fuel while such an engine is turned off flows from the reservoir barrel 80 through the orifice 90 and the main fuel filter 18 and leaks back into the fuel in the fuel tank 12, which leak is associated with the orifice 90. , Until the gravity head differential pressure between the fuel tank level and the reserve fuel level in the reservoir barrel 80 is to some extent. Since this differential pressure due to gravity is smaller than the differential pressure due to the suction of the pump when the pump assembly 32 draws the reserve fuel through the orifice 90, the leakage flow rate when the engine is turned off is determined by the pump suction. Much smaller than reserve flow. Therefore, the supply of reserve fuel will keep the engine running, even while the pump inlet is depleted of fuel, for an extended period of time, for example when the car is stopped at a low level in the fuel tank 12 on a steep hill. Maintained to be used to restart.

In addition, when the engine (and therefore also the pump) is turned off and the tank level is low, leakage from the reservoir cylinder occurs and reserve fuel flows from the orifice 90 into the filter chamber 56 and through the holes in the filter 50. It flows backward to the tank. The backflow during this stop period has the effect of washing back the main fuel filter 18 and removes most, if not all, of the entrained particles adhering to the outer surface of the filter.
Move away from the filter surface and back into the tank or disperse. This significantly reduces clogging of the main fuel filter 18, which is related to service life.

Again, as will be apparent from the following description and drawings, the fuel pump module assembly 10 is as disclosed in the aforementioned US Pat. No. 5,257,916.
It can be used for turbine type rotary vane fuel pump,
It also does not disable the vapor outlet 35 of the pump assembly 32 associated with the reserve fuel reservoir cylinder. As mentioned above, such inoperability occurs if the turbine pump is installed in the reservoir cylinder. The outlet of the vapor vent outlet 35 is intended to cause the gravity pressure of the reserve fuel in its reservoir cylinder to exceed the gravity pressure of the fuel in the fuel tank 12 by a certain amount, for example a 2.5 inch head pressure. It However, in accordance with a feature of the present invention, the vapor vent outlet communicates directly with the interior of the fuel tank 12 and the exterior of the reserve barrel 26. The height of the outlet of the vapor outlet 35, which communicates with the fuel in the tank, is generally the same as the height of the inlet 16, or the heights of the outlets are slightly different from each other.
The outlet of is slightly above the opening of the inlet 16 to the tank. Only directly facing the main fuel of the tank at approximately the same height, the differential pressure between the outlet of the vapor outlet 35 and the inlet of the pump is as small as possible.

Furthermore, if the vapor vent outlet 35 is at about the same level as the opening of the pump inlet 16 to the tank, the differential pressure between them will be submerged in the reserve fuel at the device where the pump is in the reservoir barrel. It is reversed with respect to the differential pressure generated in the case of the pump 32. Of course, the tank level
When lowered below the bottom bottom inlet cap 38 of the pump housing 36, the vapor vent outlet 35 faces directly into the ambient air or vapor in the fuel tank. At such low fuel level conditions in the tank, when the filter chamber 18 is depleted of fuel as described above, that chamber acts as a capillary seal into the tank interior to reserve fuel in the fuel reserve barrel 26. The differential pressure is likewise not counterproductive to the pump's vapor removal action.

From the following description, in accordance with the present invention, the turbine vane regenerative fuel pump disclosed in US Pat. No. 5,257,916 is similarly preferred by installing it in a properly sized reservoir cylinder. It can be seen that vapor removal action characteristics are obtained. In that case, US Pat.
47,388 (incorporated by reference), the outlet of the vapor vent passage of the pump in the reservoir cylinder is at the height of the pump inlet, independent of the head pressure of the reserve fuel in the reservoir cylinder. The condition is that the outside of the reservoir cylinder is directly communicated with the inside of the tank. This is accomplished by inserting a small, flexible plastic escape tube (not shown) that is generally horizontal from the steam vent outlet 35 and has one end at which the steam vent outlet 35 exits. And the other end leads into the tank through a suitable hole in the wall of the reservoir cylinder, the outlet of the relief pipe of which is at approximately the same height as the pump inlet.

However, as shown in the first embodiment of FIGS. 1 and 2, if the electric fuel pump 14 is preferably installed outside the fuel reserve cylinder 26, such a vapor escape pipe is provided inside the tank. No need to connect. in addition,
When the fuel pump is installed directly outside the reservoir barrel inside the tank, and when the fuel supply device with more return is used, the pump is not exposed to the hot fuel returning from the engine to the reservoir barrel and the fuel tank It is rather cooled by the fuel inside. Therefore, due to the lowered temperature of the pump structure,
It tends to reduce the volatilization evaporation of the fuel in the pump chamber.

Second Embodiment FIGS. 3 to 33 illustrate a second embodiment of the present invention, which relates to the installation of a turbine vane fuel pump, which utilizes the features of the present invention to provide a tubular reservoir. However, it has the above-described vapor venting device 33, vapor venting outlet 35, and bottom inlet cap 38 incorporated therein. The pump 32 and the vapor outlet 35 are directly installed in the fuel in the fuel tank. In a second embodiment, a fuel pump, reservoir, reservoir cylinder base module assembly 110 is provided, preferably suspended for tank orientation, and dimensionally through an opening in the top 24 of the fuel tank 12. It is installed by dropping it and placed on the bottom of the pot-shaped base of the fuel tank 12.

The module assembly 110 includes the reservoir cylinder 12
0 (see in particular FIGS. 7 to 10), the upper end of which communicates with the head space inside the fuel tank 12 or the steam dome. The reservoir barrel 120 has a circular opening 124 which is the housing 9 of the bypass pressure regulating valve 22 mounted on the reservoir barrel as in the assembly 10 of the first embodiment described above.
It houses six cylindrical portions 94.

The module assembly 110 further includes a base assembly 130 (generally illustrated in FIGS. 3-6,
Details are shown in FIGS. 11-18), which are generally cylindrical in shape and can be slid when the module is inserted through a tank mounting opening (not shown) in the tank top wall 24. It is a possible size. The base assembly 130 is open-bottomed and has four equidistantly circumferentially spaced legs 132 on its outer periphery for mounting on the pan or bottom plate 70. The base assembly 130 is a disc-shaped flange body 133.
From there, a spider leg-shaped mounting boss portion 134 that is integrally opened specially upward is projected. Boss 13
4 retains a centrally raised reservoir barrel mounting ring 136 which projects below the bottom wall 142 of the reservoir barrel 120 forming an opposing bottom outlet 144.
It has an inner hole 138 that accommodates 0. Base assembly 13
0 is snap-fitted to the lower end of the reservoir barrel 122 by mounting the reservoir barrel neck 140 within the ring 136. The module assembly 110 further includes the turbine fuel pump 14. The reservoir cylinder 120 has a special shape (for example, a tall cylinder having a small diameter),
For the pump 14 that is laterally offset with respect to the base assembly 130 and is housed in a nested relationship along one side of the reservoir barrel 120, a space is provided on the outer side surface for receiving. The incorporated electric fuel pump 14 is a base assembly 1
Without protruding beyond the outer dimensions of 30, the module assembly 110 can be mounted through an opening in the top wall of the tank even when the electric fuel pump 14 is incorporated as part of the module assembly 110.

The flat plate wall 146 of the flange body 133 in the pump recess adjacent the reservoir barrel 120 has a flange-shaped neck 148 which accommodates a rubber packing seal (not shown) to stop rotation. The base assembly 130 is snap-fitted to the reservoir barrel 120 and the pump inlet boss 16 is press-fitted and sealed to the flange neck 148 via packing to accommodate the pump 1.
4 is preassembled in the reservoir cylinder 120, and the lower end of the pump is installed on the base assembly 130. Flange body 13
A drain gutter 150, which projects upward, extends horizontally, and has an open top, is formed on the third wall 146 as shown in detail in FIGS. 13 to 17. The gutter extends from the curved tank wall 152 to the outlet end that opens. Its outlet end is a circular hole 156 in the flange wall 146.
Is connected to the edge. The electric fuel pump 14 is the flange body 1.
When installed on the gutter 33, its vapor outlet holes 35 are lined up on the inclined plate 158 of the gutter 150, and the fuel pushed out of the pump chamber 33 of the pump 32 through the outlet 35 is guided to the gutter 150. Flange opening 1 by the gutter
Sent to 56.

In addition to the flange body 133, the base assembly 130, as best shown in the exploded perspective views of FIGS. 11 and 12, and shown in detail in FIGS. 19-33.
The remaining components of the filter diaphragm 160
A heat-sealed ring-shaped diaphragm holder 162 covering the outer peripheral edge of the filter diaphragm 160, and a spring cup 164 having a centrally calibrated orifice 166.
And a compression coil spring 168 having an upper coil encased in a folded flange 166 of the cup 164.
Spring holding material 170 and ring-shaped main filter holding material 172
, A main filter support 174, and a disc-shaped main filter. The aforementioned components of the base assembly 130 are of the geometry and structure found in the detailed designs of FIGS. 19-33 and are dimensioned in relation to each other as seen in the perspective views of FIGS. 11 and 12. There is. It is also the flange body 133
The stacking and assembling relationship is illustrated. The base component is shown in its final assembly in FIGS.

Referring to FIG. 5 in connection with FIGS. 11-33, a flange body 133 having an annular flange 180 (see also FIGS. 15 and 16) forming a through hole 156 in the flange wall 146 is illustrated. . The diaphragm holder 162 has a filter diaphragm 160 attached to its outer edge and is press-fitted to the annular flange 180. The filter diaphragm 160 has a neck portion 1
The opening 156 is covered just below the flared annular end 182 on the underside of 40. A coil spring 168 is assembled to the coil spring holding member 170, and the bottom portion of the coil spring is seated on a spring seat 182 having a central hole that is recessed below the coil spring holding member 170. Spring cup 16
4 is placed on the coil top of the coil spring 168, the peripheral flange 169 of which faces downwards. This coil assembly is press fit and clamped with diaphragm retainer 162 at the position shown in FIG. 5 and inserted upward into flange 180.

The main filter 176 is the filter holding member 1.
Appropriately adhered to the underside of 72 at its outer end by heat welding or other method. The filter support member 174 is a wheel-like open grid having a doubled ring and inner rings 192, 198, properly centered on the top surface of the filter 176 seen in FIGS. 5 and 6. Fixed together. The main filter assembly is a telescoping press fit and is housed in an annular mating seat by a peripheral flange ring or skirt member 184 that surrounds the outer edge of the wall 146. Main filter 176
The assembled state of the holding member 172 and the supporting member 174 are shown in FIGS. 5 and 6.

Thus finally assembled, the base assembly 130 of the module assembly 110 is, in use, placed on the bottom wall 70 of the pan 112 (or, as is conventional, the fuel tank). Is also placed on the bottom plate). The space below the flange wall 146 and above the main filter 176 is the main filter chamber 186. The chamber 186 communicates with the fuel pump inlet 116 and the space below the second filter diaphragm 160 through the open spokes of the spring retaining member 170. Pot-shaped part 112
The main fuel flow path from the fuel inside to the chamber 186 passes through the gap between the rising leg portion 132 and the upper end of the skirt member 184, further passes through the main filter 176, and the chamber 18
It leads to 6. A second, parallel fuel flow path from the tank and pan to the main filter chamber 186 is provided by four wide openings between the four spider legs 188 of the boss portion 134 of the base assembly 130 from the filter diaphragm. 160
Of the filter support member 174 and between the spokes 190 of the loop. Furthermore, as mentioned above,
By-pass fuel from the vapor vent, via the vapor vent 35, is directed by the gutter 150 to the opening 156, flows downward through the filter diaphragm 160 and into the main filter chamber 186.

The upward movement of the main filter 176 is limited by the filter support member 174 which abuts the underside of the seven erecting legs 194 in the outer frame 192, that is, the seat 182 of the spring holding member 170. It is restricted by a ring 198 from the inside of the filter holding member 170 that contacts.

In one alternative version of the module assembly 110, the spring cup 164 is provided with a central calibrated orifice 166, which is aligned with the circular central area 161 of the diaphragm 160. With the orifice 166, the fuel flow path from the fuel reservoir 121 of the reservoir barrel 120 is opened, and the lower flow is through the necked outlet 144 on the base, through the center of the filter diaphragm 160, and then Downward through orifice 166 and through the coil gap of spring 168 to filter chamber 186.

As an alternative, when the spring cup 164 is completely open except for its calibrated orifice 166, a spring 168 is provided against the annular valve seat at the reservoir barrel outlet formed by the necked end 182. The outlet 144 can be completely closed and sealed when the filter diaphragm 160 is deflected. The complete sealing action of this valve can also be achieved by molding a suitable rubber seal material into which the filter mesh member of the filter diaphragm 160 is embedded in this non-perforated rubber material. The central portion 161 of the filter diaphragm 160 has a spring cup 16
4 functions as a valve closing member without holes. Each shape of the spring cup 164 functions to prevent the filter diaphragm 160 material from being excessively worn or torn by the end coils of the coil spring. In use,
Module assembly 110 of fuel pump and reservoir cylinder
Is mounted in the fuel tank 12 and has a generally vertically installed reservoir cylinder 120 with a main filter 176 disposed directly adjacent to the pan 112 or the bottom plate 70 of the fuel tank. , Preferably installed on it.
In normal use, the fuel tank is at least partially filled with fuel, such as gasoline, and has reached a level above the secondary filter diaphragm 160 and the main filter 176, with these filters and pump inlet 16 ,
It is completely submerged in the fuel of the tank or at least in the fuel of the pan 112.

In normal operating conditions of the pump assembly 14, fuel is drawn from the fuel in the tank and passes through the filter 176 or filter 160 to the main filter chamber 186 and from there to the pump inlet 16. A variable fuel flow is discharged from the pump outlet 42 through line 24 at an approximately constant pressure, such as 50 psig, to an engine main feed pipe (not shown). Further, the bypass pressure adjusting valve 22 bypasses and returns the fuel that has exceeded the fuel demand of the engine, and maintains a substantially constant output pressure. The regulator valve removes the excess fuel from the outlet 28.
Through the reserve chamber 121 of the reservoir cylinder 120.
To the upper part of. During normal operation of the pump, the fuel in the reservoir barrel 120 rises to a level near or somewhat below the open top 122 of the reservoir barrel 120. In some normal operating conditions, during extended engine idle or low load operating conditions, fuel rises to the top of the reservoir barrel 120 and overflows the upper end 122 of the reservoir barrel into the fuel in the pan 112 or It flows to the fuel side on the pan.

When the fuel level in the tank is low, the pump inlet 16 uses the remaining fuel in the tank as the main filter 17.
6 and secondary filter 160 may be depleted. This occurs when the above-mentioned vehicle is turning around a corner or the tank is tilted. Fuel is also depleted in the filter screen mesh of both filter 160 and main filter 176, but is still wet with fuel. In such a state, when the air in the main tank is drawn toward the pump by suction of the pump, the air tries to pass through these filter materials. However, these moist filters do not allow the passage of air due to the liquid capillary action seals of these filter materials. Chamber 1 below filter diaphragm 160 generated by pump
The pressure drop at 86 also therefore causes the filter to act as a diaphragm, moving it downwards. This movement compresses the spring 168 and lowers the filter member 160 downwardly from its neck seat 182 to provide a relatively large outlet 144.
Therethrough for communication between the reservoir chamber 121 and a region of the upper surface of the filter 160. Reserve fuel flows rapidly from the reservoir barrel outlet, laterally through diaphragm 160, into main filter chamber 186 and then to the inlet of the pump. This maintains the flow of fuel to the engine and does not disrupt the capillary sealing action of filter 176 and filter 160 due to the force balance. When the fuel in the fuel tank is re-enabled and the main filter 176 is submerged in the fuel, its capillary sealing action is broken in the main filter 176, thereby passing the fuel through the main filter 176 and into the pump in the chamber 186. Allowed to send to the entrance. This inflow reduces the downward pressure differential acting on the secondary filter diaphragm 160.
Further, when the diaphragm 160 is submerged in the fuel in the tank again, the capillary sealing function of the filter 160 is also broken. This causes the spring 168 to push the filter 160 upward and return it to its original position near the reservoir barrel outlet seat 182. If there is a rubber seal 161 on the diaphragm 160, it is reclosed on the seat 182 by the spring 168, stopping the flow of reserve fuel from the reservoir 121 to the pump inlet 16.

When the seal 161 is not on the filter 160, the mesh filter material pressed across the seat 182 closes the reservoir barrel outlet 144 but does not seal it. Thus, a controlled, continuous flow of reserve fuel permeates the reservoir 121 through the region 161.
Through the central portion of the spring, through the orifice 166 of the spring cup and through the gap of the coil spring 168 to the main filter chamber 186. Thus, when the fuel level in the tank is below the top of the reservoir barrel, the pump draws fuel from the reservoir and the tank in opposite proportions to maintain the reservoir barrel fuel reserve pressure in pressure balance.

In the first embodiment of FIGS. 1 and 2, the cup orifice 166 is calibrated (eg, to a diameter of 0.40 mm) to create the aforementioned pressure balance, and the best pressure of reserve fuel in the reservoir barrel 120. To minimize fuel spillage from the reservoir cylinder during normal operation of the fuel supply system.
This ensures that when the fuel from the main tank is depleted at the pump inlet, it ensures a sufficient amount of reserve bypass fuel to be drawn by the pump, and in normal pump operating conditions that are not depleted,
Optimizes double fuel bypass bypass return. In addition, reserve fuel is removed whenever the system is turned off, the vehicle engine is turned off, and whenever there is a gravitational differential pressure due to the fuel level in reservoir cylinder 120 being above the level of fuel in the tank. From the reservoir 121 through the filter 160 and orifice 166 into the main filter chamber 186 and then through the main filter 176 and secondary filter 160 into the main tank. The reserve fuel flow through these filters is the secondary filter 16
0 and a backwashing effect of the main filter 176 are produced, and there is an effect of washing out tank mixed particles entangled on the outer surfaces of these filters. Over the life of the device, the rate at which these filters become clogged is greatly reduced.

The filter diaphragm 160 is provided with the above-mentioned rubber seal member for fitting with the reservoir cylinder valve seat 182, or with a holeless spring cup 164 (orifice 16).
6 is not installed), the flow of the reservoir fuel through the bottom outlet 144 due to the gravitational differential pressure causes the spring 168 to close the filter diaphragm valve structure when the central portion 161 has no holes. , If not perfect, almost blocked. In this case, the amount of reserve fuel used to start the system can be significantly extended and ensured even at low fuel tank levels.

Further, in any type of reservoir barrel closed mode (ie, with reservoir reservoirs that are or are not always open to fuel flow through outlet 144 and orifice 166), main filter chamber 186 and filter diaphragm 160 are shown. Whenever the liquid pressure differential due to the pump acting between pulls the diaphragm 160 downward and moves it away from the outlet valve seat 182 (in the main filter 176 and the secondary filter 160 the fuel in the main fuel tank is The increased flow from the outlet 144 onto the upper surface of the diaphragm 160 (as when it is depleted), which may be much higher than that through the orifice 166, is as shown by the arrow in FIG. The fountain action is generated on the upper and outer surfaces of the filter diaphragm 160. This effect is facilitated by the cooperating geometry of filter 160. That is, the center is bulged by the spring 168, and it is dented downward from there to form a conical shape up to the edge of the filter of the diaphragm holder 162. This downward flow of fuel is directed radially outward of the central region 161 at the outlet 144,
It first flows along the outer surface of the filter 160 and tends to spread out a circular flow in the radial direction. Then, due to the differential pressure, it is sucked into the chamber 186 through the filter 160.
Thus, the fountain-like flow tends to flush out clogging by contaminants on the outer surface of the filter 160, especially in the annular region immediately adjacent the central region 161. Therefore, the secondary filter 160 does not become clogged with contaminants for longer than the main filter 176. This is because of the fountain-like cleaning effect and because the secondary filter 160 is located higher than the main filter 176, i.e., on the top of the base assembly 130 rather than below. The working effect of this device promotes the fail-safe feature. It is the main filter 17
6 to provide an auxiliary fuel internal passage from the fuel in the main tank through the secondary filter 160 in parallel with the flow through the main filter chamber 186 and then to the pump inlet 16. Therefore, even when the main filter 176 is severely clogged with tank contaminants, the fuel delivery system extends to remove the secondary filter 16 from the main fuel in the tank.
It is possible to operate by sucking the fuel only through zero.

In the device of this second embodiment of the present invention, in an empirical design, the upward displacement force of the spring 168 against the force generated by the liquid pressure difference between the fuel in the tank and the fuel in the reservoir cylinder, It is possible to change the balance with the force generated by the suction of the pump.
In addition to the flow through the
Reserve fuel flowing through chamber 60 into chamber 186,
It is possible to variably supplementally overflow the reservoir cylinder.
The flow of fuel from such a tubular reservoir 121, in the non-depleted state, may flow in parallel and at the same time in parallel with the fuel drawn from the tank through filters 176 and 160.

It should be noted that the valve structure of the filter diaphragm 160 is arranged so that it opens in the direction of flow out of the reservoir barrel outlet 144 and into the main chamber 186, likewise the fuel in the fuel tank opens the filter diaphragm 160. Located in the direction of flow through to chamber 186, fuel flows toward pump inlet 16 even in depleted and non-depleted conditions. When the pump is operated, the reservoir barrel outlet 144 tends to open in either state, but the effect changes depending on which state or how long the pump is used. Thus, the fixed calibrated orifice 166
Thus, the flow rate is changed / adjusted / amplified by the variable downward movement of the diaphragm 160. In this way, the orifice 161 and spring 168 are designed to work together to better balance the bypass fuel pressure in the reservoir tubes so that they are consistent with the operating and performance parameters of the device and are non-depleted. Bypass fuel can best be returned to the inlet of the fuel pump during normal operation at.

In fact, even if the orifice 166 is omitted and the spring cup 164 is holeless or a holeless rubber seal is installed in the central region 161 of the filter diaphragm 160, it minimizes spillage from the reservoir cylinder,
The balance of the reservoir barrel pressure level, which provides the best return of the reservoir barrel bypass fuel to the pump, is determined by the coil spring 16
8 is obtained by design selection. Thus, the spring 168 produces a very lightly upward biasing force on the filter diaphragm 160, that is, the differential pressure for opening the front and rear of the valve is due to the gravity of the fluid pressure in the reservoir cylinder and the pressure in the main tank. When it is caused only by the differential pressure, the outlet 144 is stopped by stopping the device.
Can be selected for the force required to close and close. When the main tank is empty, the fuel in reservoir cylinder 120 is only 4 to 8 inches at most. When the vehicle engine is operating and the fuel supply is operating, the increased differential pressure acting on the diaphragm 160, corresponding to the suction of the pump at the inlet 16, is added to the differential pressure due to its gravity and 1
68 may be designed such that the valve flexes and opens downward in such a condition.

Even if a non-permeable valve member is used on or corresponding to the filter diaphragm 160 and its central region 161, the cleaning effect of the filter can be obtained. When the system shuts down, spring 168 is selected to allow bypass fuel to leak from reservoir 121, eg, full to half, whenever the main tank is empty or at very low levels. This backwashing effect may not occur very often during the service life of the vehicle and the fuel supply system, but it can handle rare events and extend the service life of the fuel supply system. Furthermore, it is certain that the filter clogging is exacerbated when the fuel level in the tank is very low. This is because when the main fuel in the tank decreases, the amount of contaminants in the fuel tank is constant, so that the inflow of contaminants into the filter increases in a concentrated manner. Also for this,
It is beneficial to make the best use of double filtering the fuel through the pump in proportion to the main fuel tank level drop and prevent clogging of the fuel injectors or clogging of the downstream fuel line filters. .

The second embodiment of the present invention is practical in operation and, as seen in the apparatus of the aforementioned US Pat. No. 4,747,388, fuels the engine with the main tank depleted. Only when it is necessary to keep running
This is because the reserve fuel is drawn from the cylinder reservoir 121. The module 120 can thus supply a large amount of reserve fuel and extend the vehicle when restarting the vehicle when the tank is empty or when the fuel tank has a low level and the vehicle tilts and stops. You can drive reliably. On the other hand, when the device is stopped, the above-described backwash function of the filter works to cause the reservoir cylinder 120 to reduce the reserve capacity in the backwash flow, but both beneficial effects can be obtained to a lesser extent. It is possible. Also, placing the pump 140 outside the reservoir barrel 120 in the main fuel of the tank facilitates cooling of the pump and isolates it from hot fuel that may occur in the barrel reservoir.

Also in accordance with another of the aforementioned features of the present invention, the second embodiment thereof uses a turbine vane pump incorporating a steam venting device and can be operated in an intended and improved manner, Moreover, it is possible to realize the convenience of supplying a large amount of reserve fuel selectively from the related cylindrical reservoir as required. The outlet of the vapor vent passage 35 is located at a position slightly higher than the pump inlet 162, and is positioned laterally adjacent to the bottom of the reservoir chamber 121 of the reservoir cylinder 120. In addition, fuel in pump chamber 33, which has been filtered at least once through vapor vent hole 35, is returned to main filter chamber 186 through trough 150 and filter diaphragm 160. Therefore, additional bypass fuel through this two stage filter is prevented from returning to the pump inlet and just returning into the tank fuel and degrading the fuel. This control of the use of bypass fuel is especially beneficial in vehicle operating conditions with low tank levels or pump exhaustion.

A spring retaining disk 170 with spokes,
The filter diaphragm valve 160 and the spring 168 provide a simple and economical valve actuation mechanism for opening and closing the reserve fuel flow to the pump 14. In one mode of operation of valve 160, reserve fuel is not returned to the tank unless requested by pump 14. On the other hand, the reservoir cylinder 12
The head pressure of the fuel in zero acts to move the valve 160 away from the valve seat, thus increasing the orifice flow in the diaphragm valve 160 and / or the filter against the minimum coil spring bias of the economical spring 226. Produce backwash.

In addition, the vapor vent passage of the pump is located outside of the reservoir barrel so that when the pump is stopped, reserve fuel does not flow back and leak through the pump, thereby avoiding otherwise. Eliminates the use of a reservoir barrel with a pump inlet check valve or foot valve required to prevent leakage from the reservoir barrel through the pump vapor vent passage.

The base assembly 130 has a large number of its components formed into a flat and circular shape, so that the base assembly 130 shown in FIGS.
From a suitable suitable fuel plastic material, such as acetal (excluding the filter screen members of filter 160 and filter 176), as disclosed in Design Dimensions,
It can be molded easily and economically by injection molding. Preferably, the filter screen member is made of 70 micron mesh square mesh 6-nylon for the main filter 176 and 6 for the second filter diaphragm 160.
Made of 6-nylon square mesh with 2 micron mesh. The filter diaphragm 160, the holding body 162, the spring 168, and the spring holding member 170, which are the constituent members, are stacked and arranged in the base flange 133 in the upward direction. Similarly, the main filter constituent member holding member 172 and the base flange 184 are Overlapping the main filter 176 with the base flange 184 is economical in terms of parts, assembly and service costs. The assembly method of snap-fitting the pump and the reservoir cylinder component to the base assembly 130 contributes to reduction in manufacturing cost.

Third Embodiment FIGS. 34 to 39 show a pump / reservoir cylinder / base assembly 300 according to a third embodiment of the present invention.
It uses the same pump 14, bypass pressure regulating valve assembly 22 and base assembly 130 as the module assembly 100. However, this module assembly 300 has a modified structure of the reservoir 3 whose shape is shown in FIGS. 34 to 39.
02 is used. Reservoir tube 302 is generally D-shaped in horizontal cross section, as best shown in FIGS. 35, 38, and 39. Reservoir cylinder 30
The bottom wall 304 of No. 2 has a cervical outlet 140, which is snap fit onto the mounting neck 136 of the spider-shaped base boss 134 (FIG. 34). The main part of the vertically extending side wall of the reservoir cylinder 302 is composed of a cylindrical upper wall portion 306 and a lower wall portion 308, which are connected together by a horizontal shelf portion 310. The outer shape of the upper wall portion 306 is the same as the diameter of the flange body 133, and the maximum width of the reservoir cylinder 302 does not exceed the width of the module assembly 300. The shape of the side wall of the reservoir cylinder 302 is recessed for the pump 14, and the pump is installed in the recess of the reservoir cylinder 302. To this end, the reservoir tube 302 has two upper chordal walls 312, 314, which are ledge wall portions 316, 3;
At 18 they are respectively connected to the corresponding lower chordal walls 320, 322. The upper chordal walls 312, 314 are generally flat and parallel to the axis of the pump 14.

The recess for the side wall of the reservoir barrel adjacent the pump 14 is formed by the concave pocket wall 324, 326 facing the pump 14, which is joined by a wall 328 of T-shaped cross section. (Figs. 35, 38,
FIG. 39).

The pump 14 fits into the space between the wall portions 324, 326 and is mounted on the base assembly 130 in a similar manner and in a similar manner as the module assembly 110. However, the flange 100 of the bypass regulating valve 122 is shown in FIG.
A corresponding T-shaped wall 3 as best shown in FIG.
It fits into a cavity of 28 T-section in a downward sliding manner. The T-shaped lock fit by this sliding insertion is between the flange 100 of the regulating valve and the T-shaped cross section 328 of the reservoir cylinder wall.
The connection support state of the upper side of the pump and the reservoir cylinder is generated. Snapping them together and placing them on the base assembly 130 creates a mating support with the lower module. T
The profile section 328 has a notch 330 that is open at the top and receives the cylindrical portion 94 of the pressure adjustment housing 96. The regulating valve outlet 28 thus projects to the top of the reservoir barrel 302 and is spaced from the facing surface of the top wall cross section 306,
It is aligned with the reservoir cylinder outlet 144 in the extension direction.

In this manner, the reservoir tube 302 maximizes utilization of the upper space of the base assembly 130, thereby increasing the bypass reserve fuel capacity of the module assembly 300. For example, when the base flange body 133 has an outer diameter of 5 inches and the reservoir barrel 302 is made in the shape of FIGS. 34-39 in relation to the base assembly 130, the reservoir barrel is about 700-750. Can have milliliter reserve capacity. Meanwhile, the reservoir cylinder 120 is configured as shown in FIGS. 3 to 6, and FIGS.
When it is made in the shape of 0, the base flange body 133
Have the same diameter but have a capacity of about 300 milliliters. Therefore, although the reservoir cylinder 302 is somewhat more costly in terms of material and fabrication costs than the reservoir cylinder 120, the large increase in reserve capacity requires a relatively small outer diameter module and The benefit-to-cost ratio is economical for many applications when installed in small tank openings. In addition, the module assembly 11
The above-mentioned features and conveniences of 0 are also obtained in the module assembly 300.

Fourth Embodiment FIGS. 40, 41, and 42 illustrate a fourth embodiment of the present invention which also utilizes the features of the present invention for mounting a turbine vane fuel pump. With a vapor venting device incorporated outside but in close proximity to the shaped reservoir,
The pump and its vapor outlet are installed directly in the main fuel in the tank. In this fourth embodiment, the fuel pump / reservoir tube module 410 is bottom-mounted and recessed, and is installed through the opening 412 in the top wall 24 of the tank 12. The module 410 has a generally cylindrical flange cover body 414, which is used as a mounting seat for the module 410. Cover 4
14 has a peripheral flange 416, which is the top wall 2 of the tank.
4 and is suitably removably sealed and secured and is closed at its top by a top wall 418.

The module 410 has a reservoir cylinder 420, which communicates on its open upper end 422 with the internal head space of the cover 414 and with the head space of the tank 12 or the steam dome. The reservoir cylinder 420 has a slot 424 and is provided with a guide finger member 42 of the cover 414.
8 slanted pawls 426 are received, whereby the cover 4
The reservoir cylinder 420 having 14 is displaced in the circumferential direction, while allowing the head 414 to expand and contract in the vertical direction during the bottom placing operation of the reservoir cylinder 420.

The module 410 also includes a base assembly 430.
And the assembly is generally cylindrical in shape and its radial shape allows the module to be inserted and slid through the opening 412 in the top wall 24 of the tank. Base 4
30 is open at the bottom and has open edgings or legs 432 that snap onto the bottom wall 70 of the tank. The base 430 has a partition or intermediate wall 433 from which a specially shaped mounting boss 434 integrally projects upward. The base 434 has a cap member 43 on the inner shoulder 438.
6 and a sheet of second filter material 438 is captured between the cap 436 and the shoulder 438 and covers the reservoir barrel outlet opening 440 formed by the upwardly projecting neck 442 of the cap 436. ing. Base 43
0 is assembled by snap-fitting to the lower end of the outer shell 420 of the reservoir cylinder.

Module 410 also includes a turbine fuel pump 450. The reservoir cylinder 420 has a special shape and has a space for fitting the outer side portion of the pump 450 to be housed therein. So that the pump is fitted. When the pump 450 is pre-assembled as part of the module 410,
This allows the module 410 to be within the tank top opening 412.

The reservoir cylinder 420 has, for example, an indented flat portion 454 and an outward indented curved surface portion 456 (FIG. 41), and the reservoir portion 4 below the reduced cross-sectional area.
52 is formed and extends below the middle shelf 458 (FIG. 42). The recessed wall portion 454 forms a space for installation in which a conventional fuel level sensing transmission unit 458 (FIG. 42) is installed. The transmitting unit 458 has a conventional level-sensing float 460, which is attached to an arm member 462 that pivots to the unit 458 in a conventional manner. The arm member 462 is swingable and the float 460 is dropped under the module 410 as it is inserted through the tank opening 412. The lower end of the reservoir portion 452 has a bottom wall 464, which sits on the end cap 436 and which cap neck 44.
It has a central neck 466 that receives zero. The boss 434 has slots 468, 470 which define the outer shell portion 45.
The two claws 472 and 474 are received, and the bottom end of the reservoir cylinder 420 is snap-fitted to slide on the boss 434.

The base wall 434 in the pump recess region of the reservoir barrel 420 is formed with a flanged opening 479 to receive a rubber packing seal 480 to stop rotation. When the base 430 snap fits into the reservoir barrel 420, the pump inlet boss 482 also press fits and seals the packing 480 to position the lower end of the pump on the base 430 (pump 450 pre-covers cover 414). After being assembled).

The pump 450 has a pump outlet extension pipe 484 extending upward from its upper end, and a head member 486 of a diameter reducing pipe opening at its upper end 488 is attached to the extension pipe (FIG. 42). The cover 414 has a downwardly extending cylindrical boss 490 which holds a U-shaped cup-shaped sealing member 492 which is press-fitted to the lower end of the boss 490.
Is held at the lower end of its boss. A compression coil spring 496 is packaged on the head member 486, and both ends of the compression coil spring 496 abut on a holding member 494 and a shoulder portion 498 formed at a joint portion of the outlet pipe 484 and the head member 486. The spring 496 generates a force that pushes the expanding and contracting reservoir outer shell 420 downward against the cover 414 toward the bottom of the tank. Then, the pressing force causes the reservoir cylinder to be displaced and held at the bottom of the tank.

The space between the cap 436 and the partition 433 in the base structure 430, when assembled, is the valve chamber 50.
0, the chamber of which communicates with the lower reservoir chamber 502 of the reservoir barrel 420 through the opening 440. The space below partition 433 and above bottom wall 70 communicates with diaphragm filter flow chamber 50 that communicates with pump inlet 482.
4 is formed. Conventional plastic mesh filter membrane 5
06 is fixed to the inner surface of the frame 432 at its peripheral edge and covers the bottom of the chamber 504.

A perforated stiffening disk 508 covers most of the central area of the filter 506, but allows fuel to pass through the main area of the filter. Disk 508
Is preferably in the form of a wheel with open spokes, the hub 510 of which is a circular ring 51 with spokes 512.
Connected to four. The outlet valve 520 of the cylindrical reservoir is disposed in the chamber 500 and has a frame that is a valve member, and the frame has an annular valve seat 52 that projects upward from the bottom wall 434.
Sit on 2. The valve 520 has a valve stem 524 that abuts and fits over the hub 510 of the disc, and the valve and disc move together in response to the vertical deflection of the filter 506. In normal operation, when the fuel in the tank is at least at the lower end of the module 410, the conical coil spring 526 is trapped between the lower shoulder seat of the wall 434 and the upper surface of the hub 510 and the disc 508. Therefore, the filter 506 is biased downwardly with respect to the tank wall 70.

As best shown in FIGS. 41 and 42, the cover 414 has three integrated fluid flow fittings which are external to the tank and upward from its top surface and It extends laterally and is applied to a return fuel supply system. The tank relief fitting 540 has a conventional off-the-shelf stop valve (not shown) to vent the tank dome to the outside through the head space inside the cover 414. The fuel pump outlet fitting 542 has a fitting at its inner end that connects to the inlet end of a suitable fuel line hose 544 that leads to the inside of the cover boss 490 and leads to the main fuel feed pipe 546 of the vehicle engine 548. (Fig. 40). The fuel return fitting 550 connects the bypass fuel return line hose 552 to the head space of the module 410. A conventional bypass pressure regulating valve 554 is mounted between the fuel supply line 544 and the bypass line 552, downstream of the main feed pipe 456, preferably in the intake manifold 556 of the engine 548. The regulator valve 554 operates like the bypass pressure regulator valve 22 described above, regulates the fuel pressure delivered to the main fuel feed pipe 546, and the line 55.
The fuel is diverted through 2 and returned to the reservoir barrel 420 of module 410. Suitable electrical connectors (not shown) for the electric motor of the pump assembly 450 and for the fuel level sensor 458 are provided on the tank flange cover assembly 41.
Set to 0.

The fuel pump assembly 450, like the pump assembly 14, includes a turbine vane rotary pump that includes a pumping chamber 33 and a relief passage 35.
42 (shown in phantom in FIG. 42) and operates as previously described for pump assembly 14.

In use, the fuel pump and cylinder module 410, together with the reservoir cylinder 420,
, Generally installed vertically, the main fuel filter 506
Is located proximate to the bottom wall 70 of the fuel tank and is preferably located above the bottom. In normal use, the fuel tank is at least partially filled with a liquid fuel, such as gasoline, to a level above the filter 506, with the filter and pump inlet 482 completely submerged in the fuel in the tank. ing.

As in the first embodiment, during normal operation of the pump 450, fuel is drawn from the fuel in the tank through the filter 506 to the pump inlet 482 and the extension pipe at the pump outlet seals the boss 490. It is discharged to the void. It is then sent through the fitting 542 and line 544 to the fuel main feed pipe 546 at a substantially constant pressure, eg, 50 psig. Also, the regulating valve 554 maintains a substantially constant output pressure. By diverting back a portion of the fuel that was excessively supplied to engine 548, the regulator valve causes the bypass excess fuel to pass through its outlet through line 55.
It is discharged to the upper reservoir chamber 503 of the reservoir cylinder 420 via the metal 2 and the metal fitting 550. In normal operating conditions of the pump, the fuel in the reservoir barrel rises near or somewhat below the open top 422 of the reservoir barrel 420. In certain normal operating conditions, for example, when the engine is idling for extended periods of time or operating at low load, fuel rises to the upper end 422 of the reservoir barrel 420 and creates a large space between the reservoir barrel portion 452 and the cover 414. It flows downwards and into the main fuel in the tank.

With a low fuel level in the tank, the remaining fuel in the tank will remain in the main filter 50 when the vehicle is turning a corner and / or while the tank is leaning heavily.
Flowing out of 6, pump inlet 482 is depleted. The filter screen diaphragm 506 is also depleted of fuel but is still wet with fuel. In this state, when the suction force of the pump draws the air toward the pump inlet in the main tank, air tries to pass through the filter member. However, a moist filter blocks the passage of air due to the liquid capillary seal of its wet filter member. The pressure drop across the filter 506 caused by the pump actuates the filter as a diaphragm that moves it upwards. This movement compresses the spring 526 and causes the valve 520 to move to the valve seat 5
22 and up to establish communication between the valve chamber 500 and the filter chamber 504. Reserve fuel then flows downwardly from the reservoir cylinder, laterally through chamber 504 to pump inlet 482 to maintain fuel flow to the engine. When the main fuel in the tank becomes available again and the filter diaphragm 506 sinks, its capillary sealing action is broken, causing the spring 526 to push the filter diaphragm 506 back into its original position adjacent the bottom wall 70 of the tank, and the valve 520 causes valve seat 522 to close again, and reserve fuel fluid pressure stops the reserve fuel from flowing to the pump inlet and filter 506 when the pump does not require it.
To prevent loss of reserve fuel from the reservoir through to the tank.

Therefore, in the fourth embodiment of the present invention, only when the main tank pump is depleted and the engine needs fuel, as in the device of the aforementioned US Pat. No. 4,747,388. , Reserve fuel is drawn from the tubular reservoir. The module 410 also has a large reserve fuel capacity, for example 1 liter, which can extend the operation of the vehicle when the tank is empty, and when the fuel tank is tilted at a low level and stopped. Can be restarted. Although denting the sidewalls to accommodate the pump 450 and the sensor 458 reduces the volumetric capacity of the reservoir barrel 420, mounting the pump 450 outside the reservoir barrel does not allow the pump to be placed inside the reservoir barrel. Since the excluded part of the pump when mounted is eliminated, the loss of the reservoir cylinder capacity is almost recovered. Also, pump 4
Placing 50 directly in the main fuel of the tank facilitates cooling of the pump and isolates it from the hot fuel conditions in the tubular reservoir.

Also according to one of the above-mentioned main features of the invention, the fourth embodiment can be used in a turbine-blade rotary pump, which pump has an integrated steam escape device, which device is intended. It is operable in the manner just described and facilitated, yet still has the advantage of a large reserve fuel supply that can be selected from the tubular reservoir as needed. The outlet of the vapor escape passage 35 is at a height just above the pump inlet 482, and the reservoir barrel 42
It is laterally adjacent to the bottom region of the zero reservoir chamber 502. In addition, positioning the pump vapor escape passage outside the reservoir barrel eliminates the reverse leakage of reservoir fuel through the pump when the pump is stopped, thereby allowing the pump vapor escape passage from the reservoir barrel to pass through. It prevents leaks and obviates the otherwise required construction of a check valve or foot valve type reservoir barrel at the pump inlet.

Disc 508 with spokes and valve 52
0 and the spring 526 make the valve drive mechanism that opens and closes the flow of reserve fuel to the pump 450 simple and economical.
The actuation of valve 520 ensures that reserve fuel is not lost by transfer into the tank when it is not needed by pump 450. The fuel head pressure of the reservoir cylinder 420 is
Acting in the direction to close the valve 520, the spring 526 is a light coil spring that requires minimal pressing and is inexpensive.

Fifth Embodiment FIGS. 43 to 49 show a fifth embodiment of a fuel pump and reservoir cylinder module assembly 600 according to the present invention, which is used in a non-returning fuel supply system. ing. The module 600 includes a suitable tank flange cover assembly 602, which assembly is similar in construction to the cover 414 described above, and includes a reservoir barrel 604 and a base assembly 6.
06, and turbine blade type electric fuel pump assembly 608
And a conventional bypass pressure regulating valve mounted on the base outside the reservoir barrel 604 and mounted at the outlet of the pump assembly 608, and a float ball check valve and filter provided in the reservoir barrel 604. And a basket assembly 612. The reservoir cylinder 604 has the cover 60 as described above.
Fit in 2 towards the bottom of the tank. Pressure control valve 6
The outlet pipe 614 of the boss-shaped housing portion 6 of the cover 602.
A flexible tube in base 617 (FIG. 48), which is slidably and slidably inserted into 16 and used as a cover 414, is used to connect the pump outlet to a connector in cover 602. Good. The bypass pressure adjusting valve 610 is
Bypass fuel from pump assembly 608 to reservoir cylinder 60
4 has a bypass outlet 618 that is directed to discharge to a reservoir chamber 620, which is similar to the operation of the bypass pressure regulating valve 22 of the first embodiment.

Like the reservoir barrel 420, the reservoir barrel 604 has a recessed side wall 622 to allow the module 600 to
The pump assembly 608 is fitted and mounted therein within the entire outer width of the pump assembly. Top cap 40 of pump assembly 608
Is installed via a suitable sealing packing 624 (see FIG. 48), with the outlet 625 on the upper side of the pump projecting into the weir wall 629 of the reservoir barrel on the shelf 627 of the reservoir barrel recess. The pump inlet fitting 626 of the lower end cap 38 is sealed with a press fit and inserted into the packing member 628 of the base assembly 606 when the base assembly is installed on the bottom of the reservoir barrel 604. As previously mentioned, the pump assembly 608 has a rotary pump 630 and includes a pumping chamber 632 and an associated escape passage 634, which are shown in phantom in FIG.

According to one of the features of the fifth embodiment module 600, the base assembly 606 is press fit to the reservoir barrel 604 and the pump assembly 608. The base 606 is designed to be economically mass producible from injection molded plastic parts and is the preferred structure for use with the module 410 instead of the base 430. The base 606 has a circular, non-perforated upper wall 640 and has an upwardly projecting valve seat 642, which seats the reservoir cylinder 6.
No. 04, the annular boss 6 integrally formed in the bottom wall 648.
It is fitted and press-fitted in the annular frame 644 of 46. O-ring 650 surrounds boss 642 and is captured between frame 644 and shoulder 652 of boss 642. The poppet valve 654, like the valve 520, has a boss 642 seat 65.
Flange 65 that functions as a valve body that closes downward on 8
6. The valve 654 has a valve stem 660 that fits within a central bore 662 of the boss 642. The coil spring 664
The upper end of the boss 642 is mounted on the projection 666 for holding the boss 642 and surrounds the valve rod 660.
Its lower end is installed on the shoulder of 8. The upper end of the valve stem 660 is attached to the head 670 of the valve 654 after the valve stem and coil spring have been assembled to the body 640. The base assembly 606 also includes a main filter body 680, which is illustrated in FIG. 45 and whose partially enlarged views are illustrated in FIGS. 46 and 47. The filter body 680 is a circular plastic mesh filter screen sheet 682.
And has the mesh size and the material of the filter sheets of the main filters 506 and 50 described above. Preferably, the outer peripheral portion 684 of the filter screen 682 is injection molded of plastic and is molded into an annular plastic mounting ring 686. The mounting ring 686 has a downwardly sloping integral lip 688 directed radially inward, which lip extends over the annular portion of the seat 682 to the plastic material of the ring 686. The cone angle A (FIG. 46) of the lip 688 is
It is preferably about 30 degrees. Wheel-shaped disc-shaped holding member 6
90, like the retaining member 508, is centered on and covers the main area of the filter screen 682.
The disc 690 has a hub boss 692 that projects upwardly from its center and is assembled into abutment for cooperating with the lower end 668 of the valve stem 660. Each of the eight disc spokes 694 is integrally connected radially to the annular frame 696 of the disc 690 from the hub 692 (FIG. 45). Preferably, the material of the filter screen 682 is 30 micron mesh square weave 6 / 12-nylon and the material of the mounting ring 686, like the disc 690, is 6 / 12-nylon. The disc 690 has a leg protrusion 696 protruding downward.
Each leg 696 is inserted into the screen 682 and the disc 690 is heat or plastic welded to the filter screen 682.

The lower side of the body 640 is of a somewhat concave structure, sloping upward toward the pump inlet 626 and having an annular groove 700 (FIG. 44) in which a mounting ring is mounted. 680 is press-fitted and accommodated. Preferably, plastic welding protrusions 702, 704 for engagement
Are respectively provided on the rings 686, and the upper surface of the groove 700 is
A ring 686 is axially overlapped and fitted to the main body 640,
Welded by ultrasonic welding.

The base assembly 606 also includes a plastic injection molded protective ring 706 that, when placed on the bottom wall 70 of the fuel tank, covers the filter screen 682 and provides a fixed support for the module 600. There is. The protection ring 706 has an annular drainboard shape and has an L-shaped periphery.
It has a shaped flange 708 and is press-fitted and mounted around the body 640 (FIG. 43). Protective ring 70
6 has a row of downwardly inclined spokes or ribs 710, which at an angle that complements the angle A, the flange portion 7
08 extends radially inward and merges at its inner end with a unitary flat annular disc 712. Annular disc 71
2 covers the outer edge of the disk 690 from the lower side in the radial direction,
The leg 696 is stopped at the radially inner end 714 with a space on the radially outer side.

When the base portion 606 is assembled to the reservoir cylinder 604 and the pump assembly 608, the base portion is press-fitted and held by the protrusion 646 of the reservoir cylinder by the boss portion 642, and the pump inlet 626 is press-fitted by the packing 628. . As best shown in FIGS. 48 and 49, the filter and check valve assembly 612 of the module 600 preferably has a second cylindrical filter screen 720 and a float check valve ball 722. Are housed in a ribbed cage 724 that is closed on the top side,
It has a cylindrically open bottom 726, the bottom of which is press-fitted onto the upper end of a mounting boss 646, which boss has a valve 6
It is located upstream of 54 and has a valve seat plate 728 captured therebetween.

The operation of the module 600 of the fifth embodiment is as follows.
It is almost the same as module 410, except that
The bypass pressure adjusting valve 610 is installed inside the reservoir cylinder 604 and discharges directly to the cylindrical reservoir 620, which is similar to the operation of the pressure adjusting valve 22 of the module 10 of the first embodiment. Reservoir valve 654 is optionally driven by diaphragm filter 682 and associated stiffening disc 690, similar to diaphragm 506, disc 508, valve 520 of module 110 described above.

However, the addition of the check valve assembly 612 inside the reservoir chamber 620 causes the fuel level in the reservoir to drop and the float valve ball 722 to move to its seat 72.
Fuel and / or air when pumping 6
08 cannot be pulled further from the reservoir 620. Therefore, even when the filter diaphragm 682 lifts and opens the valve 654, the pump 608 cannot suck air into the pump. If not, the reservoir 620 will be completely empty.

For example, if the vehicle runs out of gas due to "gas shortage", that is, the main fuel tank 12 and the reservoir cylinder 604.
Both run until they are empty, and then a small amount of fuel is injected into the tank (from a 1 gallon reserve gasoline can), and the filter screen 682 is partially clogged with tank debris and debris. Also, when the pump assembly 608 is restarted, the filter 682 is pulled upwards to fully open the reservoir valve 654.

In such a condition, if the reservoir check valve 722 were not present to close the gap between the pump and the reservoir barrel chamber 620, the pump would draw air from the reservoir barrel and start to pump liquid from the main tank. Unable to start fuel pumping.

[0084]

The reserve fuel in the reservoir cylinder is kept in a state where it does not overflow by the bypass fuel return line in the normal operating condition, and all advantages of the reservoir in the tank are maintained.
It works with all the advantages of turbine vane fuel pumps, while facilitating the self-steaming capability of the steam venting device incorporated within the pump. In addition, the reservoir cylinder supplies fuel to the pump through the main fuel inlet filter when fuel flow from the main fuel tank is interrupted. The fuel flowing during the interruption is doubly filtered and the entry of air and fuel vapors into the pump inlet is prohibited during the interruption of the fuel supply from the tank. The reservoir barrel and pump assembly is small, sturdy, durable, reliable, relatively easy to manufacture and assemble, and has a long service life.

[Brief description of the drawings]

FIG. 1 is a perspective view of a first embodiment of a fuel supply tubular reservoir and pump assembly installed in a fuel tank of an automobile vehicle according to an embodiment of the present invention.

FIG. 2 is a partially enlarged side view of a pump reservoir cylinder assembly having the partially broken cross section of FIG.

FIG. 3 is a schematic cutaway view of a second embodiment of the fuel supply tubular reservoir and pump module assembly of the present invention.

FIG. 4 is a top view of a fuel pump reservoir cylinder of the second embodiment.

FIG. 5 is a cutaway enlarged side view of FIGS. 3 and 4, also showing the diaphragm type regulating valve in a closed state including the central cross section and having an outlet filter at the bottom of the reservoir barrel.

FIG. 6 is a view similar to FIG. 5, with the valve in the open position.

7 is a side view of the reservoir cylinder shown in FIGS. 3 to 6. FIG.

FIG. 8 is a sectional view taken along lines 8-8 in FIG. 7;

9 is a bottom view of the reservoir cylinder shown in FIG. 7. FIG.

10 is a cutaway enlarged sectional view of a portion of FIG. 8 surrounded by a circle 10. FIG.

11 is an exploded perspective view of a base assembly of the module assembly of FIGS. 3-10. FIG.

12 is another exploded perspective view of the base assembly shown in FIG. 11, but from a different angle.

FIG. 13 is a side view of the flange body of the base assembly of FIGS. 3-12 in enlarged dimensions.

FIG. 14 is a top view of the flange body.

FIG. 15 is a sectional view taken along lines 15-15 of FIG. 14;

FIG. 16 is a sectional view taken along lines 16-16 of FIG. 14;

FIG. 17 is a sectional view taken along lines 17-17 of FIG. 14;

FIG. 18 is a bottom view of the flange body of FIG.

FIG. 19 is a plan view of the filter diaphragm body of the base portion.

20 is a cross-sectional view taken along the line 20-20 of FIG.

FIG. 21 is a plan view of a diaphragm retainer of the base assembly, shown in somewhat larger dimensions than the associated filter diaphragm of FIGS. 19 and 20.

22 is a side view of the diaphragm holder of FIG. 21. FIG.

FIG. 23 is a perspective view of a coil spring cup body for a filter diaphragm of its base assembly, which cup body is a replacement for the central calibrated orifice.

24 is a plan view of the coil spring cup body shown in FIG. 23 as seen from above.

25 is a cross-sectional view taken along the line 25-25 of FIG.

FIG. 26 is a plan view of a coil spring holder of the base assembly.

27 is a cross-sectional view taken along the line 27-27 of FIG.

FIG. 28 is a plan view of the main filter holder of the base assembly.

FIG. 29 is a side view of FIG. 28.

FIG. 30 is a plan view of a filter support of the base assembly.

FIG. 31 is a side view of FIG. 30.

FIG. 32 is a plan view of the main filter body of the base assembly.

FIG. 33 is a sectional view taken along the line 33-33 of 32.

FIG. 34 is a partial elevational view showing a simplified module assembly of a fuel pump and a reservoir cylinder of a third embodiment of the present invention, a partial central sectional view thereof, and a fuel pump of the second embodiment; Using a base assembly.

FIG. 35 is a top view of the assembly of FIG. 34, greatly enlarged and shown with a portion of the base broken away.

36 is a side view of the reservoir barrel of the assembly of FIG. 34. FIG.

37 is a cross-sectional view taken along the line 37-37 of FIG. 36.

FIG. 38 is a top view of the reservoir cylinder of FIGS. 34 to 37.

39 is a bottom view of FIG. 38. FIG.

FIG. 40 is a cutaway view schematically illustrating a fuel supply module and a related vehicle engine according to a fourth embodiment of the present invention.

FIG. 41 is a top view of the fuel pump reservoir cylinder module according to the fourth embodiment of the present invention.

42 is an enlarged side cross-sectional view of the fuel pump and reservoir cylinder assembly of FIGS. 40 and 41, with a portion showing a central cross-section along line 42-42 of FIG. 41.

FIG. 43 is a central cutaway sectional view of the fuel pump and the reservoir cylinder of the fifth embodiment of the present invention, which is somewhat simplified.

44 is a greatly enlarged cut-away sectional view of a portion surrounded by a circle 7 in FIG. 43.

45 is a perspective view of a diaphragm filter body used in the module of FIGS. 43 and 44. FIG.

FIG. 46 is a central cutaway sectional view taken along the line 46-46 of FIG. 45 and is a greatly enlarged view.

FIG. 47 is a central cutaway sectional view of a portion surrounded by a circle 10 in FIG. 46, which is greatly enlarged.

48 is a center cutaway sectional view of the right side portion of FIG. 43,
It shows more details.

FIG. 49 is a partially enlarged view of FIG. 48.

[Explanation of symbols]

 10 Module Assembly 12 Fuel Tank 14 Electric Fuel Pump 18 Main Filter 22 Regulator Valve 26 Reservoir Tube 30 Orifice Plate 32 Pump Assembly 34 Electric Motor 35 Vapor Extraction Outlet 52 Seat 56 Internal Chamber 66 Corrugated Stiffener 90 Orifice 92 Filter 110 Module Assembly 120 Reservoir Tube 130 Base Assembly 133 Flange Body 160 Secondary Filter 166 Orifice 168 Spring 176 Main Filter 186 Filter Chamber 300 Module Assembly 302 Reservoir Tube 410 Module 420 Reservoir Tube 430 Base Assembly 450 Pump Assembly 460 Float 500 Valve Chamber 506 Filter 526 Spring 554 Pressure regulating valve 600 Module assembly 604 Reservoir cylinder 606 Base 608 Pump assembly 61 The pressure regulating valve 664 spring 680 main filter body 682 filter 720 filter screen 722 check valve

 ─────────────────────────────────────────────────── ─── Continuation of front page (31) Priority claim number 08/643634 (32) Priority date May 6, 1996 (33) Priority claim country United States (US) (72) Inventor Kirk De Foigner United States Michigan 48732, Essexville, West Bourton Road 947 (72) Inventor Daniel A. Gilmore United States Connecticut 06107, West Hartford, Clifton Avenue 56 (72) Inventor Wayne Tea Lipinski United States Michigan 48732, Essexville, Ward Street 21 (72) Inventor David E. Mlotka United States Connecticut 06416, Cromwell, West Street 49 (72) Inventor Charles Etch Takkii United States Michigan 48726, Kas City Shuwegura Road 4681

Claims (37)

[Claims] 1. A modular assembly of a fuel pump installed in a tank and a reservoir cylinder, the electric fuel pump having an inlet and an outlet installed in a fuel tank, and an internal main filter chamber to the pump. A main filter having a plurality of holes through which fuel can flow to the filter chamber having an outlet for communicating with the inlet of the pump, the main filter being directly at the bottom of the fuel tank A fuel reservoir cylinder configured and arranged to be housed adjacent to each other and having a closed lower end generally arranged vertically in the tank; and from the reservoir cylinder through the interior of the filter chamber Flow control means at the outlet for directing the flow of fuel to the inlet of the pump directly adjacent the lower end through the lower end and the filter chamber; A pump is disposed within the module assembly adjacent the outside of the reservoir barrel, the pump axis is generally vertical, and the inlet of the pump is at the bottom end of the reservoir barrel. There is a bypass flow path that connects the outlet of the pump and the inside of the reservoir cylinder to allow a part of the fuel to pass from the outlet of the pump to the reservoir cylinder, and thereby from the fuel tank to the main filter. When the supply of fuel is temporarily interrupted, the fuel from the reservoir cylinder is configured to flow to the inlet of the fuel pump through the flow control means, the filter chamber and its outlet. Module assembly. 2. The module assembly of claim 1, wherein said flow control means comprises a restricted orifice. 3. A secondary filter disposed above the orifice for filtering fuel flowing from the reservoir barrel through the orifice, the secondary filter having an average pore size of about 60 microns or less. Module assembly. 4. The module assembly of claim 1, wherein the main filter has an average pore size of about 100 microns or less. 5. The module assembly according to claim 2, wherein said orifice has a diameter of about 5 mm (about 0.2 inch) or less. 6. The main filter comprises an outer enclosure made of a plastic filter sheet material, generally having a pair of walls facing each other in the vertical direction, and the orifice having one of the pair of walls. A flexible plate that communicates with the inside of the outer casing and is housed between the pair of walls in the outer casing and separates the other wall of the pair of walls from the orifice and the main filter. The module assembly according to claim 2, which is provided. 7. The module assembly according to claim 6, wherein the reservoir cylinder is attached to one of the pair of walls of the main filter. 8. The amount of fuel supplied from the outlet of the pump to the outside of the fuel tank is controlled by changing and controlling the amount of fuel flowing through the bypass flow passage to the reservoir cylinder while the pump is in operation. The module assembly according to claim 1, further comprising a pressure adjusting valve provided in the bypass passage for adjusting, controlling, and sending the pressure to the engine. 9. The module assembly has a structure in which a lower end of the module assembly is installed in a laterally narrow fence of a pot-shaped container at a bottom of the fuel tank, and the reservoir cylinder is relatively small in a longitudinal direction thereof. A diameter extension tube, the longitudinal axis of the tube being generally vertical in the fuel tank, the pressure regulating valve extending at least partially through the side wall of the tube and into the tube. The main filter has an extended envelope whose longitudinal and widthwise directions are in a plane perpendicular to the tube and the axis of the pump, and the module in the height direction of the pump and the envelope. 9. The module assembly according to claim 8, wherein the thickness of the module is smaller than the overall height and width of the module assembly. 10. The pump comprises a turbine impeller pump having a rotating impeller driven in a pumping chamber in which the pump rotates, and has means for forming a steam vent passage provided in a part in a circumferential direction. The means can be open at the inlet to the pumping chamber and at the outlet to the outside of the pump to push the vapor in the pumping chamber directly out of the fuel tank through the vapor vent passage, The module assembly according to claim 1. 11. The pump has a rotary pump installed outside the reservoir cylinder in the module assembly and directly placed in the fuel tank, and the pump has a mechanism for extracting steam therein. The module assembly of claim 1, wherein the mechanism is configured such that the inlet leads to the pumping chamber of the rotary pump and the outlet leads directly to the outside of the fuel tank. 12. A valve adjacent to the bottom of the reservoir cylinder that operates to admit fuel through the filter chamber and into the inlet of the pump, and when there is no liquid fuel on the outer surface of the main filter. The module assembly of claim 1, further comprising means for opening the valve. 13. The means for opening the valve comprises the main filter, the pores of the filter being configured to be closed by the capillarity action of the liquid fuel in the tank, the filter chamber from the outer surface of the main filter. 13. The module assembly of claim 12, which blocks the passage of air or water therein. 14. The reservoir cylinder is provided with a partition wall above the bottom of the reservoir cylinder, and the partition wall has an opening,
14. The module assembly of claim 13, wherein the opening has a valve seat cooperating with the valve to open and close between the bottom of the reservoir barrel and the filter chamber. 15. The valve has a valve opening / closing member movable in a space below the partition wall, and the valve is pressed against the valve seat by a head pressure of reserve fuel in the reservoir. 14. The module assembly according to 14. 16. The module assembly comprises spring means disposed within the filter chamber and operatively coupled to a diaphragm comprising the main filter to bias the valve to a closed position with respect to the valve seat. , The upward movement of the diaphragm is dependent on the pump suction exerted inside the filter chamber when closed by the capillary action due to wetting by liquid fuel and the air and / or water outside the main filter. 16. The module assembly of claim 15, wherein the biasing by the spring means is pushed back to open the valve to allow fuel to enter the pump inlet through the filter chamber from the bottom of the reservoir barrel. 17. The flow control means is located within the filter chamber and overlies the inner surface of the main filter and is centered on the main filter with respect to the pump assembly and has a perforated annular shape. A rigid disc, the valve having a poppet valve body and a valve stem connected to a central hub of the disc, for transmitting movement of the main filter to the valve through the disc. 17. The spring means of claim is disposed between the partition wall and a hub of the disc, the spring means having a coil spring surrounding the valve stem.
The module assembly described. 18. The module assembly of claim 1, wherein the pump comprises a turbine rotary vane pump. 19. The module assembly of claim 11, wherein said pump comprises a turbine rotary vane pump. 20. The main filter includes a circular filter sheet material having an outer edge portion that extends over the disk in the radial direction, and surrounds the disk, to which the sheet material is attached, radially outwardly spaced apart. A filter mounting ring having an outer edge; and a substrate having a partition wall of the reservoir cylinder and the valve seat, the substrate having an opening into which the pump inlet is fitted and mounted, the substrate including the reservoir cylinder and the pump. A laterally surrounding lower end wall of the valve having an upwardly extending boss portion forming the valve seat, the boss portion including the valve and a flow path through the valve seat controlled by the valve seat, The lower end wall of the reservoir cylinder has a boss projecting upward, the boss of the lower end wall has an opening for accommodating the boss portion of the substrate, and the substrate has an annular shape for accommodating the filter mounting ring. Has a groove and below it in front 18. The module assembly according to claim 17, wherein the filter sheet material and the disk are suspended to form the filter chamber between the substrate and the filter sheet material. 21. The flow control means directly changes the flow rate by a head differential pressure between a liquid level of fuel in the fuel tank and a bypass reserve fuel liquid level in the reservoir cylinder that exceeds the fuel level. The bypass reserve fuel can return to the pump inlet whenever the fuel level of the tank drops below the reserve fuel level in the reservoir cylinder during operation of the fuel pump. The module assembly of claim 1, wherein the reserve fuel head pressure in the reservoir cylinder is optimized to return bypass fuel to the pump inlet while minimizing overflow of reserve fuel to the tank. 22. The reservoir cylinder has a bottom outlet opening,
The flow control means includes a secondary filter diaphragm and valve means operating in association with the secondary filter diaphragm, the secondary filter diaphragm including fuel flowing from the reservoir through the bottom outlet to the filter chamber. To cover the reservoir barrel bottom outlet from below, and the valve means is biased upward in the direction of the reservoir barrel bottom outlet by a spring to filter the tank and the filter chamber. Move to a position that opens or closes a bypass reserve fuel flow from the reservoir bottom outlet to the filter chamber in response to a varying differential pressure acting downwardly on the Dyafram filter.
The module assembly according to claim 21. 23. The module assembly has a base support, the base support has an installation flange, and the fuel pump and the reservoir cylinder are installed vertically above the flange. The bottom side of the body is open and the main filter has a sheet of plastic filter material which is spaced from the open bottom of the flange between which the filter chamber is exposed to the fuel in the tank. 2. The module assembly according to claim 1, further comprising a stiffening plate formed so as to be disposed above the main filter and spaced apart from the pump inlet of the main filter. 24. A secondary filter is mounted above the main filter and spacedly mounted to the base flange to form a portion of the filter chamber therebetween, the secondary filter also providing fuel to the fuel tank. Claim 2 that is exposed
3. The module assembly according to item 3. 25. The secondary filter has a movable diaphragm, the base flange also has a perforated support, the support being disposed on the secondary filter to support the reservoir barrel, 25. The module assembly according to claim 24, wherein the reservoir bottom outlet communicates with the valve means through the support and forms a fixed valve seat that engages the diaphragm of the secondary filter to a closed state. . 26. The reservoir cylinder has an upper end opened to the fuel tank, and a lower end attached to an assembly base member to which the main filter is attached. The assembly base member communicates with a lower end of the reservoir cylinder. And, holding the main filter on the lower side, the flow control means has a restriction orifice provided in the assembly base member and opening inside the main filter, and prevents the main filter from collapsing in the filter chamber. The module assembly of claim 1 wherein said main filter has stiffener means, which is a spacer, for cleaning. 27. A valve that operates to control the bottom outlet of the reservoir cylinder to drive fuel through the filter chamber and into the pump inlet, and liquid fuel outside the first filter. A module assembly according to claim 1 including means for opening the valve in response to the absence. 28. A secondary filter is constructed and arranged to act as a diaphragm and to function as a means for opening the valve, the main filter and the secondary filter apertures being closed by the capillary action of the liquid fuel in the tank. 28. The module assembly of claim 27 configured to prevent air or water from entering the main filter from an outer surface of the filter. 29. The valve has a valve seat and an opening / closing member that moves in a space below the valve seat, and the valve is separated from the valve seat by a gravity pressure of reserve fuel in the reservoir cylinder. The module assembly according to claim 27, wherein the module assembly is displaced. 30. The module assembly includes spring means disposed in the filter chamber, the spring means coupled to the secondary filter for displacing the valve to a closed position relative to the valve seat. And, due to the capillary action due to the wetting of the liquid fuel and the presence of air or water outside the secondary filter, overcomes the bias of the spring means in response to the pump suction applied to the interior of the filter chamber. 30. The module assembly of claim 29, wherein the secondary filter moves downwardly to open the valve to allow fuel to enter the pump inlet through the filter chamber from the bottom of the reservoir barrel. 31. The flow control means comprises a rigid spring retaining disk with an annular hole centered below the inner surface of the secondary filter and fixedly disposed in the filter chamber. The valve has a central region of the secondary filter that moves in response to deflection of the secondary filter, and the spring means is disposed between the central region of the secondary filter and the central hub of the disc. 31. The module assembly of claim 30, including a coil spring that biases the valve to displace the valve toward the valve seat. 32. The main filter further has a circular filter material sheet, and the filter material sheet has an outer peripheral edge portion and a main filter retaining ring for fixing the outer peripheral edge portion,
The module assembly has a base assembly with a flange having a through hole in which the pump inlet is disposed, the flange of the base assembly laterally connecting the bottom wall of the reservoir barrel and the pump. An enclosing boss for installing a reservoir cylinder having an upwardly projecting hole is provided under the valve seat, the flange also has a flow path leading to the valve and the valve seat, and a neck of a bottom wall of the reservoir cylinder is provided. The portion projects downward from the lower end of the reservoir cylinder and is housed in the base flange installation boss to connect the base flange to the reservoir cylinder. The base flange has an annular peripheral wall, and the peripheral wall is the main wall. 31. The module assembly of claim 30, wherein a filter retainer is housed and installed to suspend the main filter sheet beneath it to form the filter chamber therebetween. 33. The module assembly has a reserve fuel flow control means from the reservoir cylinder to the pump inlet, the flow control means being in the reservoir cylinder above and above the fuel level in the fuel tank. Directly change the flow rate by the head differential pressure with the bypass reserve fuel liquid level of
During operation of the fuel pump, whenever the fuel level in the tank drops below the reserve fuel level in the reservoir cylinder, the bypass reserve fuel returns to the pump inlet to reserve fuel head in the reservoir cylinder. The module assembly of claim 1, wherein the pressure is optimized to return the bypass fuel to the pump inlet while minimizing the overflow of reserve fuel into the tank. 34. The reserve fuel flow control means comprises a secondary filter diaphragm, the secondary filter diaphragm communicating with the tank and the filter chamber, covering the reservoir cylinder bottom outlet from below, and from the reservoir cylinder to the filter chamber. A valve for filtering fuel flowing through the secondary filter diaphragm, the valve operating in association with the secondary filter diaphragm and biased upwardly in the direction of the reservoir barrel bottom outlet, the valve occurring between the tank and the filter chamber. Move to a position to open and close a bypass reserve fuel flow from the reservoir bottom outlet to the filter chamber in response to a varying differential pressure acting downwardly on the secondary filter diaphragm.
The module assembly according to claim 33. 35. The fuel supplied from the outlet of the pump to the outside of the fuel tank by changing and controlling the amount of fuel flowing through the bypass flow passage to the reservoir cylinder during operation of the pump. 34. The module assembly according to claim 33, further comprising a pressure regulating valve provided in the bypass passage for regulating, controlling and sending the pressure to the engine. 36. The means for opening the valve comprises a secondary filter in communication with the fuel in the filter chamber and the fuel tank, the secondary filter acting as a diaphragm, the pores of the filter being the liquid fuel in the tank. 28. The module assembly of claim 27, which functions to close the capillarity of the filter to prevent air or water from passing into the filter chamber from outside the primary and secondary filters and to open the valve. 37. The module assembly includes a spring disposed in the filter chamber, the spring for biasing the valve to close the reserve fuel flow from the reservoir cylinder. Of the secondary filter elastically yields to the movement of the secondary filter, capillarity due to the wetting of the liquid fuel and air and / or water on the tank side of the secondary filter outside the diaphragm. The presence of a pump suction force inside the filter chamber overcomes the bias of the spring to open the valve and allow fuel to enter the pump inlet through the filter chamber from the reservoir cylinder. 36. The module assembly according to 36.