CA1182356A - Electromagnetically controlled fuel injection pump - Google Patents
Electromagnetically controlled fuel injection pumpInfo
- Publication number
- CA1182356A CA1182356A CA000386834A CA386834A CA1182356A CA 1182356 A CA1182356 A CA 1182356A CA 000386834 A CA000386834 A CA 000386834A CA 386834 A CA386834 A CA 386834A CA 1182356 A CA1182356 A CA 1182356A
- Authority
- CA
- Canada
- Prior art keywords
- fuel
- valve
- plunger
- spill port
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
ABSTRACT
A compact fuel injection pump of the radial plunger type having a plunger barrel that integrates the plunger and a delivery valve in a common bore along with a fuel inlet-spill port in the wall of the barrel, the port being controlled by a ball valve actuated by a solenoid to a closed position to permit pressurization of the fuel for injection past the delivery valve, the ball valve being self-aligning.
A compact fuel injection pump of the radial plunger type having a plunger barrel that integrates the plunger and a delivery valve in a common bore along with a fuel inlet-spill port in the wall of the barrel, the port being controlled by a ball valve actuated by a solenoid to a closed position to permit pressurization of the fuel for injection past the delivery valve, the ball valve being self-aligning.
Description
z~5~;
ELECTROMAGN~TICALLY CONTROLLED FUEL INJECTION PUMP
This invention relates in general to a fuel injection pump for an internal combustion engine of the spark ignition type. More particularly, i~ relates to one that is compact, lightweight, economical to construct, and relatively simple in design.
The fuel pump of the invention is of the radial plunger, spill port type with an excess of fuel always delivered to the pumping chamber. Injection is consummated by controllably blocking a spill port to permit a buildup of 10 pressure sufficient to open a conventional retraction type delivery valve and inject fuel through a fuel injection nozzle into the engine combustion chamber.
The previous use of mechanical components ~or spill type fuel injection pumps usually required the additional elements of a metering sleeve with a helix thereon, and injection timing controls, such as speed advance and cold start retard mechanisms and other control devices, to provide the desired fuel delivery characteristics to match the air flow characteristics of the engine. The use of an electromagnetically controlled fuel pump eliminates the need for such matchiny and, therefore, eliminates the need for the above additional elements.
The present invention relates to an electromagnetically controlled pump of the radial plunger type utilizing a cam on a short engine driven camshaft, the c~m being provided with acceleration and deceleration ramps to provide the desired characteristics to the pumping cycle. The plunger barrel assembly serves three functions; namely, to house the pumping plunger at one end; to incorporate a fuel delivery valve at the opposite end without the necessity of a separate housing, and to provide a machined spill valve seat in the wall of the barrel at a location between the plunger and delivery valve. The spill port is controlled by a valve that is universally seatable and self-aligning. It is actuated by an electromagnetic means, in this case a 35~
solenoid, that is constructed to assure a proper alignment of the valve in the barrel seat.
Other features of the inven~ion are the use of a formed thin gauge leaf spring that encompasses the plunger barrel not only to bias the ball valve away from its seat, but also to grasp the ball in a manner to hold it in position.
The use of electromagnetic means to control fuel injection pumps of the spill port type is not new per se in the prior art. ~or example, U.S. 3,779,2~5, Watson et al, shows a radial plunger type pump having an electromagnetically controlled spill port. However, the pumping plunger is not integrated with the delivery valve and the spill port in the compact manner indicated in the invention to be described, nor is the spill port control valve of the self-aligning type.
U.S. 3,880,131, Twaddel et al, is another example of a radial plunger type pump with an electromagnetic means for controlling a spill port. ~owever, the plunger is not integrated with the delivery valve in the barrel of the pumping unit, nor is the electromagnetically operated valve of the self-aligning type for cooperation with a spill port in the barrel of the housing.
Other examples of electromagnetically controlled valves in cooperation with fuel injection pumps are shown and described in Hobo et al, U.S. 3,762,379, Omorie et al, U.S.
3,896,779, Magata et al, U.S. 3,724,436, and Ehelm, U.S.
4,059,369. Hobo et al, shows merely an on/off electromag-netically controlled valve to control the inlet supply of fuel-to a pumping plunger. The pump per se is not of the spill port type. Omorie, shows merely an on/off type electromagnetically controlled valve controlling the inlet supply of fuel to the pump as a function of a particular electrical signal from the engine. Magata et al merely shows an electromagnetically controlled valve used in a fuel injection pump. It is not of the spill port type, nor is the plunger integrated with the delivery valve and a spill port.
5~
Eheim merely shows an an/off electromagnetically controlled valve controlling the inlet supply of fuel as a function of whether the engine is on or off. The fuel flow is controlled by a helix on a metering sleeve.
Figure ~, in U.S. 1,957,435f saur, shows the axial alignment of both the plunger and a delivery valve in the barrel of the pump. This pump, however, utilizes a helix type metering valve formed on the end of the plunger for control of the fuel flow and shows none of the advantages of this invention in the use of an electro-magnetically opera~ed spill port control valve as well as the other features enumerated above.
In contrast to this prior art, in the present invention a compact fuel injection pump of the spill port type is provided having a radially extending plunger barrel assembly that contains a plunger and a delivery valve and a valve seat in the wall of the barrel that cooperates with a self-aligning spill port control valve operated selectively by an engine controlled electromagnetic means to selectively provide engine operation at the desired time as a function of various changing engine parameters.
The invention is described further, by way of illustration, with reference to the accompanying drawings, in which:
Figure 1 is a cross-sectional view of a fuel injec~ion pump constructed according to the invention;
Figure 2 is an enlarged view of a detail of Figure l; and Figures 3, 4 and 5 are views taken on planes indicated by and viewed in the direction of arrows 3-3, 4-4 and 5-5, respectively, in Figure 2.
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Figure 1 illustrates a preferred embodiment of a fuel injection pump constructed according to the invention. It is essentially a two-piece assembly consisting of a one-piece aluminum ~ousing 10 having at least one radial bore 12 within which is mounted a plunger barrel assembly 14.
The housing 10 has a central cavi~y 16 wi~hin which is received a short engine driven camshaft 18 that is rotatably mounted at opposite ends on a pair of ball bearing units 20 and 22. Housing 10 supports bearing unit 20, while bear ng unit 22 is supported within an annular cover plate 24 bolted to and closing the open side of housing 10, as shown.
A suitable oil seal 25 is provided, as shown.
Camshaft 18, in this case, is formed ~ith a single cam 26 that is eccentrically mounted for reciprocation of a pumping plunger 30 engageable ~herewith. The bottom of the plunger is flat and the plunger rides directly on the cam.
While not shown, the cam profile would consist of an acceleration ramp, a constant velocity portion (Archimedes spiral) and a deceleration ramp.
The plunger 30 is slideably mounted in one end of a constant diameter bore 32 of a hardened steel plunger barrel 34. The latter is fixedly mounted longitudinally within the housing bore 32 and keyed to housing 10 by an anti-rotation pin 36. The fuel outlets to the engine fuel injectors are arranged at the othez or upper end of bore 32.
The upper end 38 of the plunger barrel bore 32 also is formed as a housing for a fuel delivery valve 40 to seat thereagainst to block the flow of fuel to a fuel injection line 42. The delivery valve is of the retraction type having a smaller flow cutoff land 44 at its lower end of a diameter that mates with the diameter of plunger bore 32, and a second larger diameter volume retraction land 46 at its upper end that can extend into the upper end of the plunger barrel for a short distance, as shown. A spring 48 biases the delivery or retraction valve onto its seat in the barrel. ~he preload of spring 48 is controlled by a nut 50 that is threadably ~1~2356 adjustable into the upper end of housing 10 and provided with an annular seal 52 to prevent leakage of fuel out the housing.
The retraction valve operates in a known manner moving upwardly under the increased pressure of the fuel as pumping plunger 30 moves upwardly through a pumping stroke.
When the pumping plunger 30 moves downwardly during the intake stroke, the pressure of the fuel in injection line 42 will decrease to a point where the spring 48 will be able to move the retraction valve 40 downwardly into the bore 32. The first effect is for the end o~ land 44 to engage the bore and shut off the communication of fuel between bore 32 and the fuel injection line 42. The second effect upon continued movement of the valve is to decrease the residual pressure in the fuel injection line 42 by the mass of the retraction valve moving downwardly into the upper part of the plunger bore, which increases the effective volume in the spring chamber.
Housing lO is formed with a fuel annulus 54 around the upper end of the stationary plunger barrel 34. This annulus is connected to a source of low pressure fuel through a feed passage 58 intersecting an annular fuel passage 60 in turn connected to a fuel inlet supply line 62. A sleeve 63 seals the passages from leakage into cavity 16. A low pressure supply pump, not shown, would be included in the system to maintain the fuel in inlet 62 at a low pressure.
Fuel leaking past plunger 30 is vented through plunger barrel bores 62, an annulus 64, a line 65 connected to a second annulus 68, and a drain or vent line 70.
The pressurization of fuel by plunger 30 is controlled by an inlet-spill port type construction. That is, a through port 72 connects the fuel feed or supply line 58 to the fuel chamber 74 defined in bore 32 between the upper end of plunger 30 and the lower end of delivery 44. So long as spill port 72 remains open, upward movement of plunger 30 will merely move the fuel in chamber 74 out through the spill port 72 and back into the feed line 58. When the spill port 72 is closed, the upward movement of plunger 30 can then pressurize the fuel sufficient to open the delivery valve 40 for flow of fuel to and through the injection line 42.
The spill port 72 in this case is controlled by an electromagnetically controlled ball valve 75. The radially outer edge of spill port 72 is formed as a seat for the ball valve 75, which is universally seatable.
Because of manufacturing tolerances, etc. since the plun-ger barrel is installed vertically, it is very difficult to exactly align the centre line of the solenoid armature actuator 78 at right angles -to the ball valve seat con-stltuted by the spill port 72. The use of a ball valve permits a slight misalignment of the actuator 78 without inducing side forces.
As best seen in Figures 2 to 5, a cylindrically shaped spring 102 of thin gauge stock surrounds the pump plunger barrel 34 and is contained within a reduced diameter recess 104 in the barrel body. One end of the spring is punched out to form prong-like ends 106 to engage the ball valve 74 and retain it in position, normally biasing it away from the seat of the spill port 72. The opposite side of spring 102 is provided with a pair of tangs 108 that fit within a slot 110 in a cylindrical retainer spring 112. The latter also is formed of thin gauge stock to surround the plunger barrel. The upper end of the retaining spring 112 is formed with a tab 114 positionable in a small recess 116 in plunger barrel 34 for circumferentially and axially locating the spring.
In this case, until the solenoid is energized, the spring ends 106 will maintain the ball valve away from the seat of the spill port 72 and thus prevent pressuriæation of the fuel passage 42.
The ball valve is moved to a closed position against seat 72 by the armature 88 of a solenoid 90 mounted in a recess 92 in housing 10. The solenoid is located in place by an annular retainer 94 and a biasing spring member 96. Any slight misalignment of the centreline of the solenoid armature 88 with respect to the centreline of the ball valve 72 will merely result in a tangential point contact between some point on the end o~ the armature and the spherical surface 84 so that forces still are transmitted along the radius and side forces are eliminated 3~i Therefore, the force exerted by the armature will always act through the center of the ball on the spill hole.
Completing the construction, camshaft 18 in this case is adapted to be driven by an internal combustion engine, through a pulley 100 secured to the camshaft.
A gearcould be substituted for the pulley, if desired.
While only one cam and one plunger barrel assembly is indicated, it will be clear that any multiple of the same could be incorporated into the design without depart-ing from the scope of the invention. The pump designlends itself well for 4, 6 and 8 plunger arrangements because identical pumping elements and camshaft can be used while only the housing changes.
In operation, the engine driven camshaft 18 will rotate and force the plunger 30 upwardly through a pumping stroke. At the same time, an engine control, not shown, such as a microprocessor unit, for example, will cause energization of solenoid 90 causing a leftward axial movement of the armature 88 and a similar movement Of the ball valve 75. This movement, which is about .0030 inches, for example, will seat the ball valve in the spill port 72 against the force of the leaf spring 102.
Assuming the chamber 74 has previously been fi~led with fuel through line 58, the now upward movement of the plunger 30 will pressurize this fuel to a level moving the retraction or delivery valve 40 upwardly against the force of spring 48. Injection line 42 then will fill.
The injection line is adapted to be connected to a conventional fuel injector of the pressure relief type, which above a predetermined fuel pressure opens to inject fuel into the engine proper. In this case, therefore, pressurization of fuel chamber 74 to a level sufficient to open the fuel injector will effect passage of fuel ou~ through passage 42.
When the engine control decides that the volume of fuel injected is sufficient for the particular load demand or other condition required, solenoid 90 will lh23~
then be deenergized. This will immediately permit the pressure of fuel in chamber 74 acting against the ball valve 75 and the force of spring 102 to move the ball valve rightwardly as seen in Figure l away from the spill port seat. This will cause a decay of pressure in chamber 74 by passage of fuel into the feed line 58. Accordingly, the pressure of fuel in line 42 will decay until a level is reached at which the force of spring 48 is sufficient to overcome the pressure of fuel on the delivery valve 40. This will allow the lower end of the valve to enter into the upper end of the plunger barrel bore 32 to shut off communication between the injection line 42 and the supply chamber 74. The continued decay of fuel pressure in chamber 74 will continue to permit the retrac-tion valve 40 to enter more of the plunger bore, thusretracting a portion of the valve out of the chamber in which the spring 48 is housed and in effect increasing the volume of the chamber and thereby decreasing the residual pressure of the fuel in line 42. This will prevent after injection or dribbling, in a known mannerO
The above cycle is repeated when the pump plunger again moves on its pumping stroke, if the solenoid is again energized. The duration of injection and the quantity of fuel injected will be determined by the length of time the solenoid 90 is energized to close spill port 72. This will be determined in accordance with design parameters and operating conditions of the engine, in a desired manner.
It will be seen from the above that the inven-tion provides a plunger type fuel injection pump of asimple construction having essentially a one-piece housing enclosing a plunger barrel assembly that incorporates a plunger and a delivery valve and a spill port all within a common diameter bore, thus providing an economical construction, and coupled with a self-aligning spill port control valve that permits slight misalignment of the valve actuator without causing side forces to act on the valve.
ELECTROMAGN~TICALLY CONTROLLED FUEL INJECTION PUMP
This invention relates in general to a fuel injection pump for an internal combustion engine of the spark ignition type. More particularly, i~ relates to one that is compact, lightweight, economical to construct, and relatively simple in design.
The fuel pump of the invention is of the radial plunger, spill port type with an excess of fuel always delivered to the pumping chamber. Injection is consummated by controllably blocking a spill port to permit a buildup of 10 pressure sufficient to open a conventional retraction type delivery valve and inject fuel through a fuel injection nozzle into the engine combustion chamber.
The previous use of mechanical components ~or spill type fuel injection pumps usually required the additional elements of a metering sleeve with a helix thereon, and injection timing controls, such as speed advance and cold start retard mechanisms and other control devices, to provide the desired fuel delivery characteristics to match the air flow characteristics of the engine. The use of an electromagnetically controlled fuel pump eliminates the need for such matchiny and, therefore, eliminates the need for the above additional elements.
The present invention relates to an electromagnetically controlled pump of the radial plunger type utilizing a cam on a short engine driven camshaft, the c~m being provided with acceleration and deceleration ramps to provide the desired characteristics to the pumping cycle. The plunger barrel assembly serves three functions; namely, to house the pumping plunger at one end; to incorporate a fuel delivery valve at the opposite end without the necessity of a separate housing, and to provide a machined spill valve seat in the wall of the barrel at a location between the plunger and delivery valve. The spill port is controlled by a valve that is universally seatable and self-aligning. It is actuated by an electromagnetic means, in this case a 35~
solenoid, that is constructed to assure a proper alignment of the valve in the barrel seat.
Other features of the inven~ion are the use of a formed thin gauge leaf spring that encompasses the plunger barrel not only to bias the ball valve away from its seat, but also to grasp the ball in a manner to hold it in position.
The use of electromagnetic means to control fuel injection pumps of the spill port type is not new per se in the prior art. ~or example, U.S. 3,779,2~5, Watson et al, shows a radial plunger type pump having an electromagnetically controlled spill port. However, the pumping plunger is not integrated with the delivery valve and the spill port in the compact manner indicated in the invention to be described, nor is the spill port control valve of the self-aligning type.
U.S. 3,880,131, Twaddel et al, is another example of a radial plunger type pump with an electromagnetic means for controlling a spill port. ~owever, the plunger is not integrated with the delivery valve in the barrel of the pumping unit, nor is the electromagnetically operated valve of the self-aligning type for cooperation with a spill port in the barrel of the housing.
Other examples of electromagnetically controlled valves in cooperation with fuel injection pumps are shown and described in Hobo et al, U.S. 3,762,379, Omorie et al, U.S.
3,896,779, Magata et al, U.S. 3,724,436, and Ehelm, U.S.
4,059,369. Hobo et al, shows merely an on/off electromag-netically controlled valve to control the inlet supply of fuel-to a pumping plunger. The pump per se is not of the spill port type. Omorie, shows merely an on/off type electromagnetically controlled valve controlling the inlet supply of fuel to the pump as a function of a particular electrical signal from the engine. Magata et al merely shows an electromagnetically controlled valve used in a fuel injection pump. It is not of the spill port type, nor is the plunger integrated with the delivery valve and a spill port.
5~
Eheim merely shows an an/off electromagnetically controlled valve controlling the inlet supply of fuel as a function of whether the engine is on or off. The fuel flow is controlled by a helix on a metering sleeve.
Figure ~, in U.S. 1,957,435f saur, shows the axial alignment of both the plunger and a delivery valve in the barrel of the pump. This pump, however, utilizes a helix type metering valve formed on the end of the plunger for control of the fuel flow and shows none of the advantages of this invention in the use of an electro-magnetically opera~ed spill port control valve as well as the other features enumerated above.
In contrast to this prior art, in the present invention a compact fuel injection pump of the spill port type is provided having a radially extending plunger barrel assembly that contains a plunger and a delivery valve and a valve seat in the wall of the barrel that cooperates with a self-aligning spill port control valve operated selectively by an engine controlled electromagnetic means to selectively provide engine operation at the desired time as a function of various changing engine parameters.
The invention is described further, by way of illustration, with reference to the accompanying drawings, in which:
Figure 1 is a cross-sectional view of a fuel injec~ion pump constructed according to the invention;
Figure 2 is an enlarged view of a detail of Figure l; and Figures 3, 4 and 5 are views taken on planes indicated by and viewed in the direction of arrows 3-3, 4-4 and 5-5, respectively, in Figure 2.
~ ,~
.
Figure 1 illustrates a preferred embodiment of a fuel injection pump constructed according to the invention. It is essentially a two-piece assembly consisting of a one-piece aluminum ~ousing 10 having at least one radial bore 12 within which is mounted a plunger barrel assembly 14.
The housing 10 has a central cavi~y 16 wi~hin which is received a short engine driven camshaft 18 that is rotatably mounted at opposite ends on a pair of ball bearing units 20 and 22. Housing 10 supports bearing unit 20, while bear ng unit 22 is supported within an annular cover plate 24 bolted to and closing the open side of housing 10, as shown.
A suitable oil seal 25 is provided, as shown.
Camshaft 18, in this case, is formed ~ith a single cam 26 that is eccentrically mounted for reciprocation of a pumping plunger 30 engageable ~herewith. The bottom of the plunger is flat and the plunger rides directly on the cam.
While not shown, the cam profile would consist of an acceleration ramp, a constant velocity portion (Archimedes spiral) and a deceleration ramp.
The plunger 30 is slideably mounted in one end of a constant diameter bore 32 of a hardened steel plunger barrel 34. The latter is fixedly mounted longitudinally within the housing bore 32 and keyed to housing 10 by an anti-rotation pin 36. The fuel outlets to the engine fuel injectors are arranged at the othez or upper end of bore 32.
The upper end 38 of the plunger barrel bore 32 also is formed as a housing for a fuel delivery valve 40 to seat thereagainst to block the flow of fuel to a fuel injection line 42. The delivery valve is of the retraction type having a smaller flow cutoff land 44 at its lower end of a diameter that mates with the diameter of plunger bore 32, and a second larger diameter volume retraction land 46 at its upper end that can extend into the upper end of the plunger barrel for a short distance, as shown. A spring 48 biases the delivery or retraction valve onto its seat in the barrel. ~he preload of spring 48 is controlled by a nut 50 that is threadably ~1~2356 adjustable into the upper end of housing 10 and provided with an annular seal 52 to prevent leakage of fuel out the housing.
The retraction valve operates in a known manner moving upwardly under the increased pressure of the fuel as pumping plunger 30 moves upwardly through a pumping stroke.
When the pumping plunger 30 moves downwardly during the intake stroke, the pressure of the fuel in injection line 42 will decrease to a point where the spring 48 will be able to move the retraction valve 40 downwardly into the bore 32. The first effect is for the end o~ land 44 to engage the bore and shut off the communication of fuel between bore 32 and the fuel injection line 42. The second effect upon continued movement of the valve is to decrease the residual pressure in the fuel injection line 42 by the mass of the retraction valve moving downwardly into the upper part of the plunger bore, which increases the effective volume in the spring chamber.
Housing lO is formed with a fuel annulus 54 around the upper end of the stationary plunger barrel 34. This annulus is connected to a source of low pressure fuel through a feed passage 58 intersecting an annular fuel passage 60 in turn connected to a fuel inlet supply line 62. A sleeve 63 seals the passages from leakage into cavity 16. A low pressure supply pump, not shown, would be included in the system to maintain the fuel in inlet 62 at a low pressure.
Fuel leaking past plunger 30 is vented through plunger barrel bores 62, an annulus 64, a line 65 connected to a second annulus 68, and a drain or vent line 70.
The pressurization of fuel by plunger 30 is controlled by an inlet-spill port type construction. That is, a through port 72 connects the fuel feed or supply line 58 to the fuel chamber 74 defined in bore 32 between the upper end of plunger 30 and the lower end of delivery 44. So long as spill port 72 remains open, upward movement of plunger 30 will merely move the fuel in chamber 74 out through the spill port 72 and back into the feed line 58. When the spill port 72 is closed, the upward movement of plunger 30 can then pressurize the fuel sufficient to open the delivery valve 40 for flow of fuel to and through the injection line 42.
The spill port 72 in this case is controlled by an electromagnetically controlled ball valve 75. The radially outer edge of spill port 72 is formed as a seat for the ball valve 75, which is universally seatable.
Because of manufacturing tolerances, etc. since the plun-ger barrel is installed vertically, it is very difficult to exactly align the centre line of the solenoid armature actuator 78 at right angles -to the ball valve seat con-stltuted by the spill port 72. The use of a ball valve permits a slight misalignment of the actuator 78 without inducing side forces.
As best seen in Figures 2 to 5, a cylindrically shaped spring 102 of thin gauge stock surrounds the pump plunger barrel 34 and is contained within a reduced diameter recess 104 in the barrel body. One end of the spring is punched out to form prong-like ends 106 to engage the ball valve 74 and retain it in position, normally biasing it away from the seat of the spill port 72. The opposite side of spring 102 is provided with a pair of tangs 108 that fit within a slot 110 in a cylindrical retainer spring 112. The latter also is formed of thin gauge stock to surround the plunger barrel. The upper end of the retaining spring 112 is formed with a tab 114 positionable in a small recess 116 in plunger barrel 34 for circumferentially and axially locating the spring.
In this case, until the solenoid is energized, the spring ends 106 will maintain the ball valve away from the seat of the spill port 72 and thus prevent pressuriæation of the fuel passage 42.
The ball valve is moved to a closed position against seat 72 by the armature 88 of a solenoid 90 mounted in a recess 92 in housing 10. The solenoid is located in place by an annular retainer 94 and a biasing spring member 96. Any slight misalignment of the centreline of the solenoid armature 88 with respect to the centreline of the ball valve 72 will merely result in a tangential point contact between some point on the end o~ the armature and the spherical surface 84 so that forces still are transmitted along the radius and side forces are eliminated 3~i Therefore, the force exerted by the armature will always act through the center of the ball on the spill hole.
Completing the construction, camshaft 18 in this case is adapted to be driven by an internal combustion engine, through a pulley 100 secured to the camshaft.
A gearcould be substituted for the pulley, if desired.
While only one cam and one plunger barrel assembly is indicated, it will be clear that any multiple of the same could be incorporated into the design without depart-ing from the scope of the invention. The pump designlends itself well for 4, 6 and 8 plunger arrangements because identical pumping elements and camshaft can be used while only the housing changes.
In operation, the engine driven camshaft 18 will rotate and force the plunger 30 upwardly through a pumping stroke. At the same time, an engine control, not shown, such as a microprocessor unit, for example, will cause energization of solenoid 90 causing a leftward axial movement of the armature 88 and a similar movement Of the ball valve 75. This movement, which is about .0030 inches, for example, will seat the ball valve in the spill port 72 against the force of the leaf spring 102.
Assuming the chamber 74 has previously been fi~led with fuel through line 58, the now upward movement of the plunger 30 will pressurize this fuel to a level moving the retraction or delivery valve 40 upwardly against the force of spring 48. Injection line 42 then will fill.
The injection line is adapted to be connected to a conventional fuel injector of the pressure relief type, which above a predetermined fuel pressure opens to inject fuel into the engine proper. In this case, therefore, pressurization of fuel chamber 74 to a level sufficient to open the fuel injector will effect passage of fuel ou~ through passage 42.
When the engine control decides that the volume of fuel injected is sufficient for the particular load demand or other condition required, solenoid 90 will lh23~
then be deenergized. This will immediately permit the pressure of fuel in chamber 74 acting against the ball valve 75 and the force of spring 102 to move the ball valve rightwardly as seen in Figure l away from the spill port seat. This will cause a decay of pressure in chamber 74 by passage of fuel into the feed line 58. Accordingly, the pressure of fuel in line 42 will decay until a level is reached at which the force of spring 48 is sufficient to overcome the pressure of fuel on the delivery valve 40. This will allow the lower end of the valve to enter into the upper end of the plunger barrel bore 32 to shut off communication between the injection line 42 and the supply chamber 74. The continued decay of fuel pressure in chamber 74 will continue to permit the retrac-tion valve 40 to enter more of the plunger bore, thusretracting a portion of the valve out of the chamber in which the spring 48 is housed and in effect increasing the volume of the chamber and thereby decreasing the residual pressure of the fuel in line 42. This will prevent after injection or dribbling, in a known mannerO
The above cycle is repeated when the pump plunger again moves on its pumping stroke, if the solenoid is again energized. The duration of injection and the quantity of fuel injected will be determined by the length of time the solenoid 90 is energized to close spill port 72. This will be determined in accordance with design parameters and operating conditions of the engine, in a desired manner.
It will be seen from the above that the inven-tion provides a plunger type fuel injection pump of asimple construction having essentially a one-piece housing enclosing a plunger barrel assembly that incorporates a plunger and a delivery valve and a spill port all within a common diameter bore, thus providing an economical construction, and coupled with a self-aligning spill port control valve that permits slight misalignment of the valve actuator without causing side forces to act on the valve.
2~5~
While the invention has been shown and described in its preferred embodiments, it will be clear to ~hose skilled in the arts to which it pertains that many changes and modifications may be made thereto without departing from the scope of the invention.
While the invention has been shown and described in its preferred embodiments, it will be clear to ~hose skilled in the arts to which it pertains that many changes and modifications may be made thereto without departing from the scope of the invention.
Claims (8)
1. A fuel injection pump of the spill port type having a housing having a central cavity therein receiving a rotatable engine driven camshaft, a stationary pump plunger barrel projecting radially from the camshaft through the housing and having a bore containing a plunger movable therein, cam means on the camshaft engageable with the plunger to move the plunger axially along its bore through a fuel pumping stroke, the barrel bore being of uniform diameter and forming at one end a housing for a spring closed fuel pressure opened fuel delivery valve contained therein and blocking the one end thereof connected to a fuel injection line, the plunger and delivery valve being axially spaced along the barrel bore to define a fuel chamber therebetween, the barrel having a fuel inlet-spill port opening through the wall of the barrel into the fuel chamber and constituting a valve seat, a source of supply fuel under a low pressure connected to the inlet-spill port, and an electromagnetically con-trolled spill port control valve movably mounted with respect to the spill port valve seat and selectively operable to control the buildup and duration of pressure in the fuel chamber to a level effecting opening of the delivery valve and injection of fuel into the injection line upon movement of the plunger through its pumping stroke, the spill port valve being self-aligning with respect to the valve seat.
2. A pump as in claim 1, the spill port valve including a ball universally seatable on the valve seat.
3. A pump as in claim 1, whereby the spill port is machined into each barrel wall.
4. A pump as in claim 2, including a solenoid engageable with the spill port valve, and spring means biasing the valve to an unseated position.
5. A pump as in claim 2, including leaf spring means biasing the ball valve onto the valve seat, the spring being formed of thin gauge material and having end portions bifurcated to engage and hold the valve in position.
6. A pump as in claim 5, the spring being essen-tially cylindrical in shape to surround the barrel and having tang retaining end portions opposite the ball valve retaining end portions.
7. A pump as in claim 6, incuding a second retain-ing spring anchored to the barrel and engaging the tang end portions of the first mentioned spring to maintain the latter spring in position.
8. A pump as in claim 2, including an actuator fixed to the ball, a solenoid having an armature engageable with the actuator, and spring means biasing the ball and actuator and armature to an inoperative position away from the ball valve seat.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000438179A CA1182357A (en) | 1980-10-06 | 1983-08-24 | Electromagnetically controlled fuel injection pump spill port valve assembly |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US19398580A | 1980-10-06 | 1980-10-06 | |
| US193,985 | 1980-10-06 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000438179A Division CA1182357A (en) | 1980-10-06 | 1983-08-24 | Electromagnetically controlled fuel injection pump spill port valve assembly |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1182356A true CA1182356A (en) | 1985-02-12 |
Family
ID=22715863
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000386834A Expired CA1182356A (en) | 1980-10-06 | 1981-09-28 | Electromagnetically controlled fuel injection pump |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0049458B1 (en) |
| JP (1) | JPS5791371A (en) |
| CA (1) | CA1182356A (en) |
| DE (1) | DE3170004D1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58183826A (en) * | 1982-04-19 | 1983-10-27 | Toyota Motor Corp | Fuel injection device for internal combustion engines |
| GB8401626D0 (en) * | 1984-01-21 | 1984-02-22 | Lucas Ind Plc | Liquid fuel injection pumping apparatus |
| DE3427730A1 (en) * | 1984-07-27 | 1986-02-06 | Motorenfabrik Hatz Gmbh & Co Kg, 8399 Ruhstorf | FUEL INJECTION SYSTEM |
| GB9306603D0 (en) * | 1993-03-30 | 1993-05-26 | Lucas Ind Plc | Fuel pump |
| GB2292423A (en) * | 1994-08-17 | 1996-02-21 | Lucas Ind Plc | Pump for fuel injection |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1664608A (en) * | 1924-05-12 | 1928-04-03 | Louis O French | Fuel-injection system |
| JPS506043B1 (en) * | 1969-05-19 | 1975-03-10 | ||
| DE2046182A1 (en) * | 1970-09-18 | 1972-03-23 | Bosch Gmbh Robert | Fuel injection device for multi-cylinder internal combustion engines |
| US3779225A (en) * | 1972-06-08 | 1973-12-18 | Bendix Corp | Reciprocating plunger type fuel injection pump having electromagnetically operated control port |
| US3880131A (en) * | 1973-06-28 | 1975-04-29 | Bendix Corp | Fuel injection system for an internal combustion engine |
| DE2503346C2 (en) * | 1975-01-28 | 1986-04-03 | Robert Bosch Gmbh, 7000 Stuttgart | Fuel distributor injection pump for internal combustion engines |
| GB2013275B (en) * | 1978-01-31 | 1982-06-30 | Lucas Industries Ltd | Liquid fuel pumping apparatus |
| JPS587842Y2 (en) * | 1978-06-30 | 1983-02-12 | ナショナル住宅産業株式会社 | Drainer for balcony |
| US4241714A (en) * | 1979-06-25 | 1980-12-30 | General Motors Corporation | Solenoid valve controlled fuel injection pump |
-
1981
- 1981-09-28 CA CA000386834A patent/CA1182356A/en not_active Expired
- 1981-09-29 DE DE8181107712T patent/DE3170004D1/en not_active Expired
- 1981-09-29 EP EP19810107712 patent/EP0049458B1/en not_active Expired
- 1981-10-05 JP JP15856281A patent/JPS5791371A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5791371A (en) | 1982-06-07 |
| EP0049458A1 (en) | 1982-04-14 |
| EP0049458B1 (en) | 1985-04-17 |
| DE3170004D1 (en) | 1985-05-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |