WO1997001031A1 - Fuel pump and method of operating same - Google Patents
Fuel pump and method of operating same Download PDFInfo
- Publication number
- WO1997001031A1 WO1997001031A1 PCT/US1996/007246 US9607246W WO9701031A1 WO 1997001031 A1 WO1997001031 A1 WO 1997001031A1 US 9607246 W US9607246 W US 9607246W WO 9701031 A1 WO9701031 A1 WO 9701031A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- control valve
- piston
- valve body
- piston valve
- interval
- Prior art date
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 46
- 238000000034 method Methods 0.000 title claims description 14
- 238000006073 displacement reaction Methods 0.000 claims abstract description 26
- 238000005086 pumping Methods 0.000 claims description 17
- 238000002347 injection Methods 0.000 claims description 15
- 239000007924 injection Substances 0.000 claims description 15
- 239000012530 fluid Substances 0.000 claims description 11
- 125000006850 spacer group Chemical group 0.000 claims description 11
- 239000002283 diesel fuel Substances 0.000 abstract description 2
- 230000000712 assembly Effects 0.000 description 4
- 238000000429 assembly Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 230000003467 diminishing effect Effects 0.000 description 2
- 230000000977 initiatory effect Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- 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
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
-
- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
- F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means
Abstract
A fuel pump (10) for a vehicular diesel fuel pump member having a control valve assembly which includes a housing having a control valve chamber (20), and an actuatable control valve (34) disposed in the control valve chamber (20). The control valve includes a piston valve body (36) axially movable over a motion displacement interval between first and second positions. The motion displacement interval is defined by first and second sub-intervals bounded by the first and second positions, respectively. The control valve assembly further includes means (32) for actuating the control valve. A valve stop (44) is disposed in the housing adjacent the control valve chamber (20), and a piston valve body seat (90) contacts the valve stop (44) whenever the piston valve body (36) is in the second position. The piston valve body seat (90) contacts a pump body seating surface whenever the piston valve body is in the first position.
Description
FUEL PUMP AND METHOD OF OPERATING SAME
Technical Field
The present invention relates to a fuel pump control valve assembly and method of operating same for dampening control valve motion in a heavy duty truck diesel fuel injection system including either a unit pump or unit fuel injectors.
Background Art
Fuel control valve assemblies in vehicular fuel injection systems, typically include a housing having a control valve chamber, a control valve having a piston valve body, and a valve stop. Electromagnetic actuators are commonly used in control valve assemblies for electronically controlling actuation of the control valve. Examples are shown in U.S. Patent Numbers 4,618,095, assigned to the assignee of the present invention, and 4,501,246.
A primary disadvantage associated with existing control valve assemblies, including those with electronically actuated control valves, is the fact that upon contact of the control valve with the control valve may stop, the control valve "bounce" of the valve stop in diminishing series fashion as illustrated in Figure 6a before finally closing. This control valve "bounce" can significantly lessen the precision of the fuel flow process, and thereby the combustion efficiency.
For the foregoing reasons, there is a need for a control valve assembly that overcomes the problems and limitations of the prior art .
Disclosure Of The Invention
It is, therefore, an object of the present invention to provide an improved control valve assembly.
It is another object of the present invention to provide an improved control valve assembly for more precisely controlling valve displacement over unit time by varying the rate of displacement per unit time.
It is a further object of the present invention to provide such an improved control valve assembly for controlling fuel in fuel pumps and fuel injectors for internal combustion engines and being able to slow, and thereby dump, the control valve at the end of the injection stroke.
The present invention also contemplates such a control valve assembly wherein the damping of the control valve at one or both ends of its stroke may be controlled electronically by adjusting current levels to the control valve armature coil and the one of this control technique particularly in pilot injection type fuel injection systems thereby facilitating precise control over the initiation of the pilot injection by the precise control of the end of the preceding main injection illustrated as t2 in Figures 6b and 6c .
In carrying out the above objects and other objects and features of the present invention, a control valve assembly and method for controlling valve motion are provided. The control valve assembly comprises a housing having a control valve disposed in a control valve chamber. The control valve includes a piston valve body axially movable over a motion displacement
interval between first and second positions within the control valve chamber. The motion displacement interval is defined by first and second sub-intervals that are each bounded on one end by the first and second positions, respectively. The piston valve body includes a piston valve body seat. The piston valve body seat contacts a pump body seating surface whenever the piston valve body is in the first position.
A valve stop is disposed in the housing adjacent the control valve chamber. The piston valve body seat contacts the valve stop whenever the piston valve body is in the second position. A first control
■ valve spring resiliently biases the piston valve body toward the second position whenever the piston valve body is in the first sub-interval. A second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop whenever the piston valve body is in the second sub-interval.
In another embodiment, the control valve assembly includes means for actuating the control valve, such as an electromagnetic actuator or solenoid. The piston valve body is urged toward an actuated position whenever the control valve is in an actuated state. The actuated position can be either the first or second position, and an unactuated position is the other of the first and second positions. The first control valve spring resiliently biases the piston valve body toward the unactuated position whenever the piston valve body is in the first sub-interval . The second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop whenever the piston valve body is in the second sub-interval.
Upon deactuation of the control valve, the piston valve body is urged toward the second position, and into damped engagement with the valve stop.
Many configurations are possible for the first and second control valve springs in accordance with the present invention. For example, the first control valve spring could altematively be configured to resiliently bias the piston valve body toward the second position when the piston valve body is in the second sub- interval, in addition to whenever the piston valve body is in the first sub-interval. The second control valve spring could be configured to resiliently bias the piston valve body toward the first position when the piston valve body is in the second sub-interval, or alternatively, the second control valve spring could be configured to resiliently bias the piston valve body toward the second position when the piston valve body is in the second sub-interval. The • direction which the second control valve spring biases the piston valve body, for a particular configuration, is determined accordingly so as to bring the piston valve body into damped engagement with the valve stop.
In another configuration, the second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop when the piston valve body is in the first sub-interval, in addition to whenever the piston valve body is in the second sub-interval.
The control valve assembly of the present invention has many useful applications. One such application is to use the control valve assembly in a
fuel pump or fuel injector for a fuel injection system for an internal combustion engine.
A pump, constructed according to the present invention, comprises a pump body having a pumping chamber, a fuel inlet for supplying fuel to the pumping chamber, an output port, and a control valve chamber between the pumping chamber and the outlet port. A reciprocating plunger is disposed in the pumping chamber. The plunger is reciprocatable over a stroke range between an extended position and a retracted position. A plunger spring resiliently biases the plunger to the retracted position.
The pump further comprises an actuatable control valve for controlling fuel . The control valve is disposed in the control valve chamber, and the control valve includes a piston valve body axially movable over a motion displacement interval between first and second positions within the control valve chamber. The motion displacement interval is defined by first and second sub-intervals bounded by the first and second positions, respectively. The piston valve body includes a piston valve body seat. The piston valve body seat contacts a pump body seating surface whenever the piston valve body is in the first position.
The pump further comprises a stator assembly, and means for actuating the control valve, such as an electromagnetic actuator or solenoid, disposed in the stator assembly. The piston valve body is urged toward an actuated position whenever the control valve is in an actuated state.
An armature is secured to the control valve, and a valve stop is disposed in the pump body adjacent the control valve chamber. The piston valve body seat contacts the valve stop whenever the piston valve body is in the second position.
Further in accordance with the control valve assembly of the present invention, a first control valve spring resiliently biases the piston valve body toward the unactuated position whenever the piston valve body is in the first sub-interval. A second control valve spring resiliently biases the piston valve body into damped engagement with the valve stop whenever the • piston valve body is in the second sub-interval.
A stop plate secures the valve stop within the pump body. A stator spacer is disposed between the pump body and the stator assembly and has a central opening for receiving the armature therein. A plurality of fasteners mount the stator assembly and the stator spacer on the pump body. Upon actuation of the control valve, the piston valve body is urged to the actuated position against the biasing of the first control valve spring.
In another embodiment of a control valve assembly, a piston is received in the piston valve body. The piston has first and second ends, and a periphery surface. The first end abuts the valve stop; the second end abuts an end of the second control valve spring. The second control valve spring is received in the piston valve body. The piston has a flow passage in the form of a slot, or plurality radially and/or axially sequenced ports, for accommodating fluid flow formed on the periphery surface of the piston. The flow passage
extends from the second end toward the first end. The flow passage extends outboard of the piston valve body whenever the piston valve body is in the first sub¬ interval. The flow passage is enclosed by the piston valve body whenever the piston valve body is in the second sub-interval. When the flow passage is enclosed by the piston valve body, fluid flow is restricted thereby dampening the engagement of the piston valve body with said valve stop.
Alternatively, a method for controlling rate of displacement of the control valve is provided. In an electromagnetically actuated control valve assembly, the
• electric current can be precisely controlled to cause the piston valve body movement to model the piston valve body movement for the previously described control valve assemblies.
The advantages accruing to the present invention are numerous. For example, the control valve assembly or method of the present invention can be used in pumps or injectors having either a vertical or horizontal orientated plunger.
The above objects and other objects, features, and advantages of the present invention will be readily appreciated by one of ordinary skill in the art from the following detailed description of the best mode for carrying out the invention when taken in connection with the accompanying drawings.
Brief Description Of The Drawings
FIGURE 1 is a side elevation, partially in section, of a pump for a fuel injection system, the pump having a first embodiment of a control valve assembly made in accordance with the present invention;
FIGURE 2 is an enlarged cross-sectional view of the control valve assembly of Figure 1;
FIGURE 3 is an enlarged cross-sectional view of a second embodiment of a control valve assembly of the present invention, and showing the valve in open position (lower half) and closed (upper half) ,-
FIGURE 4a is an enlarged cross-sectional view of a third embodiment of a control valve assembly of the present invention;
FIGURE 4b is an enlarged cross-sectional view of the piston shown in Figure 4a, taken along line X-X of Figure 4a;
FIGURE 4c is a side elevation view of an alternative piston as may be employed in the embodiment of Figure 4a;
FIGURE 4d is a cross-sectional view of the piston shown in Figure 4c, taken along line Y-Y of Figure 4c;
FIGURE 5 is an enlarged cross-sectional view of a fourth embodiment of a control valve assembly of the present invention;
FIGURE 6a is a graph illustrating piston valve body displacement versus time during operation of a control valve assembly according to a method of the prior art; and
FIGURES 6b and 6c is the present invention as depicted by all its embodiments, including the mechanical control arrangements of Figures 2-5, and the electronic control arrangement described herein.
Best Modes For Carrying Out The Invention
Referring now to Figure 1, a pump 10 including a first embodiment of a control valve assembly made in accordance with the present invention is illustrated. The pump 10 has a pump body 12, and a pumping chamber 14 is enclosed by pump body 12. A fuel inlet 16 for supplying fuel to pump 10 is located on the periphery of pump body 12. Pump body 12 further has an outlet port 18, and a control valve chamber 20 between pumping chamber 14 and outlet port 18. Passageways 22 and 24 connect pumping chamber 14, control valve chamber 20, and outlet port 18, respectively.
A reciprocating plunger 26 is disposed in pumping chamber 14. Plunger 26 is reciprocatable over a stroke range between an extended position indicated at A and a retracted position indicated at B. A plunger spring 28 resiliently biases plunger 26 to the retracted position B.
A stator assembly 30 contains an electromagnetic actuator 32, such as a solenoid. An electromagnetically actuated control valve 34 is disposed in control valve chamber 20 for controlling
fuel. Control valve 34 includes a piston valve body 36. Piston valve body 36 is movable between an unactuated position and an actuated position within control valve chamber 20. Control valve chamber 20 contains passageways 38 for fuel flow. An armature 40 is secured to control valve 34 by a fastener such as a screw 42.
A valve stop 44 is disposed in pump body 12 adjacent to control valve chamber 20. An O-ring 46 encircles valve stop 44 to prevent fuel leakage. A stop plate 48 secures valve stop 44 within pump body 12.
A stator spacer 50 having a central opening 52 • for receiving armature 40 therein is disposed between pump body 12 and stator assembly 30. Stator spacer 50 has notches 54 for receiving a retainer 56. O-rings 58 seal stator spacer 50 against stator assembly 30 and pump body 12. Fasteners 60 mount stator assembly 30 and stator spacer 50 on pump body 12.
With reference to Figures 1 and 2, the control valve assembly will be further described. Piston valve body 36 is axially movable over a motion displacement interval between first and second positions within control valve chamber 20. The actuated position of piston valve body 36 is one of the first and second positions, and the unactuated position is the other of the first and second positions. Piston valve body 36 is urged toward the actuated position whenever control valve 34 is in the actuated state. The motion displacement interval for piston valve body 36 is defined by first and second sub-intervals defined by the first and second positions for piston valve body 36, respectively.
A first control valve spring 70 resiliently biases piston valve body 36 toward the unactuated position whenever piston valve body 36 is in the first sub-interval. A spring seat 72 and retainer 56 abut first and second ends of first control valve spring 70. A second control valve spring 76 resiliently biases piston valve body 36 into damped engagement with valve stop 44 whenever piston valve body 36 is in the second sub-interval . Valve stop 44 includes a valve stop base 78 and a valve stop head 80. A pin 82 retains valve stop head 80. Second control valve spring 76 encircles pin 82 and is held between valve stop base 78 and the valve stop head 80.
With further reference to Figure 1, an engagement surface 86 engages a reciprocal drive member, such as a cam 88. The reciprocal motion imparted to engagement surface 86 is transferred to plunger 26 in a conventional manner.
With continuing reference to Figures 1 and 2, piston valve body 36 is axially movable over the motion displacement interval between the first and second positions. Piston valve body 36 includes a piston valve body seat 90. Seat 90 contacts a pump body seating surface 91 whenever pisto valve body 36 is in the first position and contacts valve stop head 80 whenever piston valve body 36 is in the second position.
First control valve spring 70 is resiliently biasing the piston valve body 36 toward the unactuated position whenever piston valve body 36 is in the first sub-interval of the motion displacement interval. Second control valve spring 76 resiliently biases piston valve body 36 toward either the first position or the
second position so as to resiliently bias piston valve body 36 into damped engagement with valve stop 44 whenever piston valve body 36 is in the second sub¬ interval of the motion displacement interval.
As shown in Figure 2, the second position of piston valve body 36 is the unactuated position. First control valve spring 70 resiliently biases piston valve body 36 toward the unactuated position, that is, toward valve stop head 80. Second control valve spring 76 resiliently biases piston valve body 36 to slow and dampen the engagement of piston valve body 36 with valve stop head 80.
With reference to Figure 3, a second embodiment of a control valve assembly will be described. A pump body 92 has a fuel inlet 94, a control valve chamber 96, and passageways 98 and 100 for fuel flow. A control valve 102 having a piston valve body 104 is disposed in control valve chamber 96. Passageways 106 are provided for fuel flow.
An armature 108 is secured to control valve
102 by a fastener, such as a screw 110. A valve stop 112 is disposed in pump body 92 adjacent control valve chamber 96. Piston valve body 104 contacts valve stop 112 whenever piston valve body 104 is in the second position, as shown in the lower half of Figure 3. An O- ring 114 encircles valve stop 112. A stop plate 116 secures valve stop 112 within pump body 92.
A stator spacer 118 has a central opening 120 for receiving armature 108 therein. Stator spacer 118 has notches 122 for receiving a retainer 124. O-rings
126 seal stator spacer 118 against pump body 92 and
stator assembly 30. A first control valve spring 128 resiliently biases piston valve body 104 toward valve stop 112. A seat 130 is provided for first control valve spring 128. Second control valve spring 132 is concentrically disposed with first spring 128 and resiliently biases piston valve body 104 toward valve stop 112. Second control valve spring 132 is provided with a seat 134 on the control valve 102.
The second position for piston valve body 104 is the unactuated position. The first control valve spring 128 resiliently biases piston valve body 104 toward the unactuated position, that is, toward valve
■ stop 112. Seat 130 is shaped so that first control valve spring 128 biases piston valve body 104 whenever piston valve body 104 is in the first sub-interval. The second control valve spring 132 resiliently biases piston valve body 104 toward valve stop 112 to slow and dampen the engagement of piston valve body 104 with valve stop 112. Seat 134 is shaped so that the second control valve spring 132 always biases piston valve body
104 in the first and second sub-intervals.
With reference to Figures 4a and 4b, a third embodiment of a control valve assembly will be described. A pump body 140 has a control valve chamber 142, and passageways 144 and 146. A control valve 148 having a piston valve body 150 is disposed in control valve chamber 142. Passageways 152 are provided for fluid flow.
A piston 154 having a flow passage in the form of a slot or flat 155 on its periphery, is disposed in piston valve body 150. A valve stop 156 is disposed in pump body 140 adjacent control valve chamber 142. An O-
ring 158 encircles valve stop 156. A stop plate 160 secures valve stop 156 within pump body 140. A second control valve spring 162 is disposed within piston valve body 150. Second control valve spring 162 has a seat 164.
As shown in Figures 4c and 4d, the flow passage may be provided by boring the piston 154 from one end only and provided radial directed flow passages 165 in fluid communication with the bore 163.
As piston valve body 150 approaches the second position, flow passage 155 is closed off. By reducing the fluid flow, a dampening effect is created.
With reference to Figure 5, a fourth embodiment of a control valve assembly is shown. A pump body 170 has a control valve chamber 172, and passageways 174 and 176. A control valve 178 having a piston valve body 180 is disposed in control valve chamber 172. Passageways 182 are provided for fluid flow. A cylindrical valve stop 184 is disposed in pump body 170. An O-ring 186 encircles valve stop 184. A stop plate 188 secures valve stop 184 within pump body 170. Passageway 190 is provided in valve stop 184 for fluid flow. A second control valve spring 192 is provided for dampening the engagement of piston valve body 180 with valve stop 184. A seat 194 abuts an end of second control valve spring 192.
Operation of pump 10 will now be described with reference to Figure 1. Fuel is received from a fuel supply by fuel inlet 16. The cam 88 drives engagement surface 86. Plunger 26 is moved from the
retracted position B to the extended position A, and fuel is pressurized within pumping chamber 14.
Control valve 34 is controlled by electromagnetic actuator 32, and allows pressurized fuel to be directed through outlet port 18 by way of passageways 22 and 24.
Referring to Figure 6a, there is shown a graph of piston valve body displacement versus time during operation of the control valve assembly according to a method of the prior art. In the full closed position, the piston valve body seat contacts the pump body seating surface. In the full open position, the piston valve body seat contacts the valve stop. At time t, the solenoid current is discontinued and the piston valve body is urged from the full closed position toward the full open position, initially contacting valve stop at time t2, experiencing thereafter some degree of bounce off the valve stop in cyclic diminishing fashion as shown.
According to the present invention as shown in
Figures 6b and 6c, at time t2, the second control valve spring comes into play, either exclusively as shown in Figure 6b or jointly with the first valve spring, as shown in Figure 6c, thereby urging the piston valve body into a delayed, damped engagement with the valve stop. In the prior art, without a second control valve spring, or equivalent dampening means, such as the above- described piston with flow passage arrangement, valve "bounce" is observed as the piston valve body settles into engagement with the valve stop.
Alternatively, by precisely monitoring the current through the electromagnetic actuator, the mechanical control valve assembly can be modeled electrically. Further, damping of the control valve at one or both ends of its stroke is controllec electronically by adjusting current levels to the control valve armature coil and the one of this control technique particularly in pilot injection type fuel injection systems thereby facilitating precise control over the initiation of the pilot injection by the precise control of the end of the preceding main injection illustrated as t2 in Figures 6b and 6c.
Additionally, one may use any one of theh embodiments described in Figures 2 through 5, or its equivalent, in combination with the technique of adjusting the current levels to the control valve actuating coil.
With reference to Figures 2-5, the motion displacement interval and defining sub-intervals for the piston valve body will now be further described. In the first sub-interval, the piston valve body is held in the first position either by the first control valve spring or the induced force from the electromagnetic actuator. If the piston valve body is held in the first position by the first control valve spring, then by actuation of the electromagnetic actuator, the piston valve body is urged toward the second position. If the piston valve body is held in the first position by the induced force from the electromagnetic actuator, then the piston valve body is urged toward the second position by the first control valve spring upon deactuation. As the piston valve body approaches the second position in either one
of the previously described manners, the piston valve body moves through the first sub-interval.
Upon entering the second sub-interval, the piston valve body is in close proximity with the valve stop. In the second sub-interval, the second control valve spring, being configured to apply force in the appropriate direction to bring the piston valve body into dleayed engagement with the valve stop, resiliently biases the piston valve body. Alternatively, as previously described, the control valve assembly can be provided with the piston-auxiliary fuel flow arrangement, or further controlled electrically.
It is to be understood that while the forms of the invention described above constitute the preferred embodiment of the invention, the preceding description is not intended to illustrate all possible forms thereof. For example, it will be recognized that many design features of the foregoing unit pump are equally applicable to a unit fuel injector, as shown for example in U.S. Patent Number 4,618,095 assigned to the assignee of the present invention, and incorporated herein by reference. By referring herein to a pump, applicant includes a unit fuel injector. It is also to be understood that the words used are words of description, rather than limitation, and that various changes may be made without departing from the spirit and scope of the invention, which should be construed according to the following claims.
Claims
1. A pump for a fuel injection system, the pump comprising: a pump body having a pumping chamber, a fuel inlet for supplying fuel to said pumping chamber, an output port, and a control valve chamber between said pumping chamber and said outlet port; a reciprocating plunger disposed in said pumping chamber, said plunger being reciprocatable over a stroke range between an extended position and a retracted position; a plunger spring for resiliently biasing said plunger to the retracted position; an actuatable control valve for controlling fuel, said control valve being disposed in said control valve chamber, and said control valve including a piston valve body axially movable over a motion displacement interval between first and second positions within said control valve chamber, said motion displacement interval being defined by first and second sub-intervals bounded by said first and second positions, respectively; a stator assembly; an electromagnetic actuator for actuating said control valve, said electromagnetic actuator being disposed in said stator assembly, wherein said piston valve body is urged toward an actuated position whenever said control valve is in an actuated state, said actuated position being one of said first and second positions, and an unactuated position being the other of said first and second positions; an armature secured to said control valve; a valve stop disposed in said pump body adjacent said control valve chamber, said piston valve body contacting said valve stop whenever said piston valve body is in said second position; a first control valve spring for resiliently biasing said piston valve body toward said unactuated position whenever said piston valve body is in said first sub-interval; a second control valve spring for resiliently biasing said piston valve body into damped engagement with said valve stop whenever said piston valve body is in said second sub-interval. a stop plate securing said valve stop within said pump body; a stator spacer disposed between said pump body and said stator assembly and having a central opening for receiving said armature therein; and a plurality of fasteners mounting said stator assembly and said stator spacer on said pump body, whereby upon actuation of said control valve, said piston valve body is urged to the actuated position against the biasing of said first control valve spring.
2. The pump of claim 1 wherein said actuated position is said first position, whereby upon deactuation of said control valve, said piston valve body is urged toward said unactuated position and into damped engagement with said valve stop.
3. The pump of claim 1 wherein said actuated position is said second position, whereby upon actuation of said control valve, said piston valve body is urged toward said actuated position and into damped engagement with said valve stop.
4. The pump of claim 1 wherein said first control valve spring resiliently biases said piston valve body toward said second position when said piston valve body is in said second sub-interval.
5. The pump of claim 1 wherein said second control valve spring resiliently biases said piston valve body toward said first position when said piston valve body is in said second sub-interval .
6. The pump of claim 1 wherein said second control valve spring resiliently biases said piston valve body toward said second position when said piston valve body is in said second sub-interval.
7. The pump of claim 1 wherein said second control valve spring resiliently biases said piston valve body into damped engagement with said valve stop when said piston valve body is in said first sub- interval.
8. The pump of claim 1 wherein said second control valve spring is encircled by said valve stop.
9. The pump of claim 1 further comprising: a piston received in said piston valve body, said piston having first and second ends and a periphery surface, said first end abutting said valve stop, said second end abutting an end of said second control valve spring, said second control valve spring being received in said piston valve body, said piston having a slot for accommodating fuel flow and being formed on the periphery surface of said piston, and said slot extending from said second end toward said first end, said slot extending outboard of said piston valve body whenever said piston valve body is in said first sub- interval, and said slot being enclosed being by said piston valve body whenever said piston valve body is in said second sub-interval, whereby when said slot is enclosed by said piston valve body, fuel flow is restricted thereby dampening the engagement of said piston valve body with said valve stop.
10. A method for controlling injection in a fuel pump, said pump comprising: a pump body having a pumping chamber, a fuel inlet for supplying fuel to said pumping chamber, an output port, and a control valve chamber between said pumping chamber and said outlet port; a reciprocating plunger disposed in said • pumping chamber, said plunger being reciprocatable over a stroke range between an extended position and a retracted position; a plunger spring for resiliently biasing said plunger to the retracted position; an actuatable control valve for controlling fuel, said control valve being disposed in said control valve chamber, and said control valve including a piston valve body axially movable over a motion displacement interval between first and second positions within said control valve chamber, said motion displacement interval being defined by first and second sub-intervals bounded by said first and second positions, respectively; a stator assembly; an electromagnetic actuator for actuating said control valve, said electromagnetic actuator being disposed in said stator assembly, wherein said piston valve body is urged toward an actuated position whenever said control valve is in an actuated state, said actuated position being one of said first and second positions, and an unactuated position being the other of said first and second positions; an armature secured to said control valve; a valve stop disposed in said pump body adjacent said control valve chamber, said piston valve body contacting said valve stop whenever said piston valve body is in said second position; a first control valve spring for resiliently biasing said piston valve body toward said unactuated position; the method comprising the steps of: (a) energizing the electromagnetic actuator at a first current level to initiate displacement of said control valve from one of said first and second positions to the other of said positions; and
(b) thereafter adjusting the first current level to a second current level prior to said control valve reaching said other of said positions, whereby the termination of the control valve stroke may be damped.
11. A control valve assembly comprising: a housing having a control valve chamber; a control valve disposed in said control valve chamber, said control valve including a piston valve body axially movable over a motion displacement interval between first and second positions within said control valve chamber, said motion displacement interval being defined by first and second sub-intervals bounded by said first and second positions, respectively; a valve stop disposed in said housing adjacent said control valve chamber, said piston valve body contacting said valve stop whenever said piston valve body is in said second position; a first control valve spring for resiliently biasing said piston valve body toward said second position whenever said piston valve body is in said first sub-interval; and a second control valve spring for resiliently biasing said piston valve body into damped engagement with said valve stop whenever said piston valve body is in said second sub-interval.
12. The control valve assembly of claim 11 wherein said first control valve spring resiliently biases said piston valve body toward said second position when said piston valve body is in said second sub-interval.
13. The control valve assembly of claim 11 wherein said second control valve spring resiliently biases said piston valve body toward said first position when said piston valve body is in said second sub¬ interval.
14. The control valve assembly of claim 11 wherein said second control valve spring resiliently biases said piston valve body toward said second position when said piston valve body is in said second sub-interval.
15. The control valve assembly of claim 11 wherein said second control valve spring resiliently biases said piston valve body into damped engagement with said valve stop when said piston valve body is in said first sub-interval.
16. The control valve assembly of claim 11 further comprising: a piston received in said piston valve body, said piston having first and second ends and a periphery surface, said first end abutting said valve stop, said second end abutting an end of said second control valve spring, said second control valve spring being received in said piston valve body, said piston having a slot for accommodating fluid flow and being formed on the periphery surface of said piston, and said slot extending from said second end toward said first end, said slot extending outboard of said piston valve body whenever said piston valve body is in said first sub- interval, and said slot being enclosed being by said piston valve body whenever said piston valve body is in said second sub-interval, whereby when said slot is enclosed by said piston valve body, fluid flow is restricted thereby dampening the engagement of said piston valve body with said valve stop.
17. A control valve assembly comprising: a housing having a control valve chamber; an actuatable control valve disposed in said control valve chamber, said control valve including a piston valve body axially movable over a motion displacement interval between first and second positions within said control valve chamber, said motion displacement interval being defined by first and second sub-intervals bounded by said first and second positions, respectively; means for actuating said control valve, wherein said piston valve body is urged toward an actuated position whenever said control valve is in an actuated state, said actuated position being one of said first and second positions, and an unactuated position being the other of said first and second positions; a valve stop disposed in said housing adjacent said control valve chamber, said piston valve body contacting said valve stop whenever said piston valve body is in said second position; a first control valve spring for resiliently biasing said piston valve body toward said unactuated position whenever said piston valve body is in said first sub-interval; and a second control valve spring for resiliently biasing said piston valve body into damped engagement with said valve stop whenever said piston valve body is in said second sub-interval.
18. The control valve assembly of claim 17 wherein said actuated position is said first position,
• whereby upon deactuation of said control valve, said piston valve body is urged toward said unactuated position and into damped engagement with said valve stop.
19. The control valve assembly of claim 17 wherein said actuated position is said second position, whereby upon actuation of said control valve, said piston valve body is urged toward said actuated position and into damped engagement with said valve stop.
20. The control valve assembly of claim 17 wherein said first control valve spring resiliently biases said piston valve body toward said second position when said piston valve body is in said second sub-interval.
21. The control valve assembly of claim 17 wherein said second control valve spring resiliently biases said piston valve body toward said first position when said piston valve body is in said second sub¬ interval.
22. The control valve assembly of claim 17 wherein said second control valve spring resiliently biases said piston valve body toward said second position when said piston valve body is in said second sub-interval.
23. The control valve assembly of claim 17 wherein said second control valve spring resiliently biases said piston valve body into damped engagement with said valve stop when said piston valve body is in said first sub-interval.
24. The control valve assembly of claim 17 further comprising: a piston received in said piston valve body, said piston having first and second ends and a periphery surface, said first end abutting said valve stop, said second end abutting an end of said second control valve spring, said second control valve spring being received in said piston valve body, said piston having a slot for accommodating fluid flow and being formed on the periphery surface of said piston, and said slot extending from said second end toward said first end, said slot extending outboard of said piston valve body whenever said piston valve body is in said first sub¬ interval, and said slot being enclosed being by said piston valve body whenever said piston valve body is in said second sub-interval, whereby when said slot is enclosed by said piston valve body, fluid flow is restricted thereby dampening the engagement of said piston valve body with said valve stop.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP96914714A EP0834013B1 (en) | 1995-06-23 | 1996-05-20 | Fuel pump |
| DE69624240T DE69624240T2 (en) | 1995-06-23 | 1996-05-20 | FUEL PUMP |
| JP9503837A JPH11508345A (en) | 1995-06-23 | 1996-05-20 | Fuel pump and operating method thereof |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US49394995A | 1995-06-23 | 1995-06-23 | |
| US493,949 | 1995-06-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO1997001031A1 true WO1997001031A1 (en) | 1997-01-09 |
Family
ID=23962383
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/US1996/007246 WO1997001031A1 (en) | 1995-06-23 | 1996-05-20 | Fuel pump and method of operating same |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0834013B1 (en) |
| JP (1) | JPH11508345A (en) |
| DE (1) | DE69624240T2 (en) |
| WO (1) | WO1997001031A1 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2335007A (en) * | 1998-03-06 | 1999-09-08 | Bosch Gmbh Robert | Fuel-injection device for internal combustion engines |
| WO2000017511A1 (en) * | 1998-09-23 | 2000-03-30 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
| US6059545A (en) * | 1995-06-23 | 2000-05-09 | Diesel Technology Company | Fuel pump control valve assembly |
| WO2000034644A1 (en) | 1998-12-11 | 2000-06-15 | Diesel Technology Company | Control valve |
| US6089470A (en) * | 1999-03-10 | 2000-07-18 | Diesel Technology Company | Control valve assembly for pumps and injectors |
| GB2350154A (en) * | 1999-05-21 | 2000-11-22 | Bosch Gmbh Robert | Fuel injection system with solenoid valve in high-pressure pump cylinder |
| DE19939459A1 (en) * | 1999-08-20 | 2000-11-23 | Bosch Gmbh Robert | Hydraulic pressure source, especially in combustion engine, having externally controllable activation element in form of Piezo-electric actuator |
| US6158419A (en) * | 1999-03-10 | 2000-12-12 | Diesel Technology Company | Control valve assembly for pumps and injectors |
| US6450778B1 (en) | 2000-12-07 | 2002-09-17 | Diesel Technology Company | Pump system with high pressure restriction |
| US6457457B1 (en) * | 1997-09-20 | 2002-10-01 | Delphi Technologies, Inc. | Control method |
| US6523526B2 (en) | 2000-04-05 | 2003-02-25 | Daimler Chrysler Ag | Method for operating a diesel engine with a pump-line-nozzle injection system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19956519B4 (en) * | 1999-11-24 | 2004-05-27 | Robert Bosch Gmbh | Device for injecting a fluid with variable injection pressure |
| JP2013053545A (en) * | 2011-09-02 | 2013-03-21 | Yanmar Co Ltd | Fuel injection pump |
| JP6547564B2 (en) * | 2015-09-30 | 2019-07-24 | ヤンマー株式会社 | Electromagnetic spill valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE4020951A1 (en) * | 1990-06-30 | 1992-01-02 | Bosch Gmbh Robert | MAGNETIC VALVE |
| GB9422742D0 (en) * | 1994-11-11 | 1995-01-04 | Lucas Ind Plc | Drive circuit |
-
1996
- 1996-05-20 WO PCT/US1996/007246 patent/WO1997001031A1/en active IP Right Grant
- 1996-05-20 DE DE69624240T patent/DE69624240T2/en not_active Expired - Fee Related
- 1996-05-20 EP EP96914714A patent/EP0834013B1/en not_active Expired - Lifetime
- 1996-05-20 JP JP9503837A patent/JPH11508345A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2770394A (en) * | 1954-05-04 | 1956-11-13 | Automatic Canteen Co | Method and apparatus for dispensing a measured amount of beverage ingredients |
| US3958902A (en) * | 1974-06-14 | 1976-05-25 | Taisan Industrial Co., Ltd. | Electromagnetic pump |
| US4501246A (en) | 1981-07-22 | 1985-02-26 | Robert Bosch Gmbh | Fuel injection pump |
| US4569641A (en) * | 1982-09-07 | 1986-02-11 | Greatbatch Enterprises, Inc. | Low power electromagnetic pump |
| US4618095A (en) | 1985-07-02 | 1986-10-21 | General Motors Corporation | Electromagnetic unit fuel injector with port assist spilldown |
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| Title |
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| See also references of EP0834013A4 * |
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6059545A (en) * | 1995-06-23 | 2000-05-09 | Diesel Technology Company | Fuel pump control valve assembly |
| US6457457B1 (en) * | 1997-09-20 | 2002-10-01 | Delphi Technologies, Inc. | Control method |
| FR2775737A1 (en) * | 1998-03-06 | 1999-09-10 | Bosch Gmbh Robert | FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINE |
| GB2335007B (en) * | 1998-03-06 | 2000-03-29 | Bosch Gmbh Robert | Fuel-injection device for internal combustion engines |
| GB2335007A (en) * | 1998-03-06 | 1999-09-08 | Bosch Gmbh Robert | Fuel-injection device for internal combustion engines |
| WO2000017511A1 (en) * | 1998-09-23 | 2000-03-30 | Robert Bosch Gmbh | Fuel injection device for internal combustion engines |
| WO2000034644A1 (en) | 1998-12-11 | 2000-06-15 | Diesel Technology Company | Control valve |
| EP1149235A1 (en) * | 1998-12-11 | 2001-10-31 | Diesel Technology Company | Control valve |
| EP1149235B1 (en) * | 1998-12-11 | 2012-05-02 | Diesel Technology Company | Control valve |
| JP2002539360A (en) * | 1999-03-10 | 2002-11-19 | ディーゼル・テクノロジー・カンパニー | Control valve assembly for pump and injector |
| US6158419A (en) * | 1999-03-10 | 2000-12-12 | Diesel Technology Company | Control valve assembly for pumps and injectors |
| EP1165957A1 (en) * | 1999-03-10 | 2002-01-02 | Diesel Technology Company | Control valve assembly for pumps and injectors |
| US6089470A (en) * | 1999-03-10 | 2000-07-18 | Diesel Technology Company | Control valve assembly for pumps and injectors |
| EP1165957A4 (en) * | 1999-03-10 | 2004-03-03 | Diesel Tech Co | Control valve assembly for pumps and injectors |
| JP2001003838A (en) * | 1999-05-21 | 2001-01-09 | Robert Bosch Gmbh | Electronic injection mechanism |
| GB2350154B (en) * | 1999-05-21 | 2001-07-18 | Bosch Gmbh Robert | Electronic injection system |
| GB2350154A (en) * | 1999-05-21 | 2000-11-22 | Bosch Gmbh Robert | Fuel injection system with solenoid valve in high-pressure pump cylinder |
| JP4612149B2 (en) * | 1999-05-21 | 2011-01-12 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Electronic injection mechanism |
| DE19939459A1 (en) * | 1999-08-20 | 2000-11-23 | Bosch Gmbh Robert | Hydraulic pressure source, especially in combustion engine, having externally controllable activation element in form of Piezo-electric actuator |
| US6523526B2 (en) | 2000-04-05 | 2003-02-25 | Daimler Chrysler Ag | Method for operating a diesel engine with a pump-line-nozzle injection system |
| US6450778B1 (en) | 2000-12-07 | 2002-09-17 | Diesel Technology Company | Pump system with high pressure restriction |
| US6854962B2 (en) | 2000-12-07 | 2005-02-15 | Robert Bosch Gmbh | Pump system with high pressure restriction |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0834013B1 (en) | 2002-10-09 |
| EP0834013A1 (en) | 1998-04-08 |
| EP0834013A4 (en) | 1999-09-22 |
| DE69624240D1 (en) | 2002-11-14 |
| DE69624240T2 (en) | 2003-06-18 |
| JPH11508345A (en) | 1999-07-21 |
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