US3810581A - Timed pulsed fuel injection apparatus and method - Google Patents

Timed pulsed fuel injection apparatus and method Download PDF

Info

Publication number
US3810581A
US3810581A US33915373A US3810581A US 3810581 A US3810581 A US 3810581A US 33915373 A US33915373 A US 33915373A US 3810581 A US3810581 A US 3810581A
Authority
US
United States
Prior art keywords
pressure
chamber
accumulator
flow
injection
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 - Lifetime
Application number
Other languages
English (en)
Inventor
S Rhine
M Showalter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ANATECH Inc
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to US05339153 priority Critical patent/US3810581A/en
Priority to GB965074A priority patent/GB1469164A/en
Priority to CA194,046A priority patent/CA1016433A/en
Priority to SE7402966A priority patent/SE404235B/xx
Priority to FR7407842A priority patent/FR2220677B3/fr
Priority to JP49026423A priority patent/JPS6035545B2/ja
Priority to DE19742411787 priority patent/DE2411787C3/de
Priority to IT2874174A priority patent/IT1019575B/it
Application granted granted Critical
Publication of US3810581A publication Critical patent/US3810581A/en
Assigned to AUTOMOTIVE ENGINE ASSOCIATES, 301 S. BLOUNT ST., CITY OF MADISON, reassignment AUTOMOTIVE ENGINE ASSOCIATES, 301 S. BLOUNT ST., CITY OF MADISON, ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SHOWALTER, MERLE R., RHINE, SAMUEL
Assigned to ANATECH, A CORP OF WI. reassignment ANATECH, A CORP OF WI. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: AUTOMOTIVE ENGINE ASSOCIATES, A LIMITED PARTNERSHIP OF WI., BY JAMES W. MYRLAND
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/16—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor characterised by the distributor being fed from a constant pressure source, e.g. accumulator or constant pressure positive displacement pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/0318—Processes
    • Y10T137/0396—Involving pressure control

Definitions

  • ABSTRACT [52] US. Cl 239/533, 123/139 AS, 137/14 [51] Int. Cl. F02m 47/02 A timed Pulsed fuel injection device which meters fuel 58 Field of Search 239/533; 123/139 AS; continuously and distributes flow pulses to nozzles 137/14 through a rotary distributor pressure cascading device which totally isolates the metering event from varia- [56 R f r e Ci tions and dynamic effects in the n injection lines.
  • pulsed fuel injection systems are required for diesel engines and stratified charge engines and are very useful in conventional spark engines, particularly when air pollution control requires very accurate metering of fuel.
  • pulsed fuel injection systems are difficult to design without metering errors due to wave effects in the system which result in dynamically caused errors (particularly for high pressure systems where the bulk modulus compressibilty of the fuel becomes important and for very highspeed systems).
  • each working part has a geometrically simple shape and a mathematically well defined and simple function (in both the static and dynamic sense), by minimizing the complexity of each working parts function, by eliminating sources of interaction between the parts which produce second order metering errors, and by assuring that the distances of fluid pressure wave travel between the metering parts of the system are so small that the desired fluid equilibrium conditions between the operating parts are achieved during the time available even at the highest system operating speed.
  • the pump has a pressurizing but not a metering function; total flow metering is done simply and continuously by a variable metering orifice across a constant pressure drop; and this total flow is divided into equal volumes and delivered in pulses by the interaction of three accumulator chambers interconnected in a pressure cascading sequence by a rotary distributor to the injection nozzles.
  • Each accumulator when it is opened to the downstream accumulator, discharges its volume as a sort of fluid capacitor, so that flow delivery even at very low engine speeds is in the form of a high speed pulse sufficient to assure good atomization.
  • the addition of adjustable throttling valves between the n accumulator chambers 31' and the nozzles produces excellent pulse shaping. Also, the continuous fuel metering device can be readily adapted with a pressure maximum to assure that fuel volume per injection pulse cannot exceed a certain set value.
  • Metered fuel flows into an accumulator chamber 1 which accumulates volume only above a certain pressure p which is in intermittant contact through a rotary distributor with an accumulator 2 once between each injection pulse.
  • Chamber 2 accumulates volume only above a pressure p p so that all fuel metered while accumulator 2 is in contact with accumulator chamber 1, as well as all volume stored in chamber 1 since the previous contact period, flows into chamber 2 during the l2 contact period.
  • chamber 2 When chamber 2 is cut off from chamber 1, it is in intermittant sequential contact through a rotary distributor with one of the n injection nozzle lines, each of which has an accumulator cham ber 31' which receives the volume accumulated in chamber 2 and stores it at a pressure p less than p The transferred volume in the chamber 31' is discharged through the ith injection nozzle.
  • Accumulator chambers l, 2, and 31' are constructed so that chamber volumes are invariant with pressures below pressures p p and p Therefore, variations in blowdown pressures between chamber 2 and the chambers 31' do not result in errors of the metering event, which occurs in the redundant interaction between chambers l and 2 and the continuous fuel flow metering system.
  • the pressure cascading system has the advantage that so long as each injection nozzle i has an adequate flow rate at a pressure below PM, the inequalities p, p p hold, and the rotary distributor seals, the system produces excellent series and cross section metering statistics over the full range operating speeds and over a wide range of the design parameters P 2, P etc. Therefore, injection nozzles and injection line lengths need not be matched, and the system can operate at ultrahigh speeds.
  • the system can be modified to produce the desirable square wave pulse shape with a maximum fuel flow per degree crank angle.
  • the system is also adapted with pressure constraint means to assure that injected volume per pulse cannot exceed a set maximum to preclude overrichening.
  • FIG. 1 shows the preferred form of accumulator device employed in the injection system.
  • FIG. 2 shows the pressure-volume relation of the type of accumulator shown in FIG. 1, and illustrates the mathematical relations required between the accumulator chambers in the injection system.
  • FIG. 3 shows the fuel flow sequence of the injection system in a block diagram.
  • FIG. 4 shows a schematic diagram of the entire injection system.
  • FIG. 5 shows a cutaway of a rotary distributor for the injection system.
  • FIG. 6 shows the structure of a needle valve pulse shaping system for the injection system.
  • FIG. 6a' is a section thru the pulse shaping needle valve. 7 I
  • FIG. 7 illustrates the flow equilibrium behavior of the needle valve pulse shaping device in interaction with the nozzle and accumulator chamber 31'.
  • FIG. 8 shows a continuous flow fuel metering system adapted with a maximum pressure setting which, when attached to the pressure cascading device, assures that fuel volume per injection pulse cannot exceed a set maximum.
  • Chart 1 summarizes in table form the design requirements and the critical interrelations of the various components.
  • a piece of rigid metal tubing including holes in its walls is sheathed by a piece of flexible elastic tubing 2 (for instance commercially available high pressure nylon hydraulic tubing) which is under substantial strain tension and grips the tubing I normally with substantial force.
  • Elastomer tubing 2 is sealed at the ends around rigid tube 1 by clamps 3, 4 so that it does not leak under internal pressure.
  • the accumulatorchamber formed by assembly 1, 2, 3, 4 has the characteristic that its fluid volume is invariant as long as its internal pressure is less than the gripping force on tube 1 generated by the strain tension of elastomer tubing 2; but when internal pressure exceeds this force, tubing 2 stretches still further and chamber volume increases with further increases in internal pressure.
  • the chamber is a very simple example of a spring accumulator chamber with a mechanical stop where the elastomer tubing 2 serves as the distensible chamber and the spring, and rigid metal tube 1 serves as the stop.
  • the accumulator chamber so formed reacts extremely quickly, can be designed using well known strength-of-materials formulas, and is both extremely durable and very inexpensive to manufacture.
  • Each of the accumulators has an accumulating pressure, below which its volume is invariant, which depends on the tension of the elastic tubing when it is against its inside tubing stop.
  • P P g a certain characteristic internal pressure
  • P accumulators l, 2, 31' have a volume invariant with pressure.
  • the chamber accumulates volume increasingly with pressure for pressures above this pres sure P While dynamic effects may cause the pressurevolume relations of the accumulators to depart to some degree from the functions of FIG. 2, it is a very good approximation, even at ultrahigh speeds, that the accumulators obey the relations shown both while pressure and volume are increasing and while pressure (and hence volume) are decreasing (accumulator blowclown).
  • chamber 1 has accumulated volume at a pressure p and suddenly comes in fluid contact with chamber 2 which is at an initial pressure below its accumulating pressure As shown in FIG. 2, so long as the accumulated volume of chamber 1 is less than VMAX all of the accumulated volume of chamber 1 will be very quickly transferred to chamber 2, where it will be stored at lower pressure p Similarly, if chamber 2 with its accumulated volume (now closed off from chamber 1) comes in fluid contact with a chamber 31', complete fluid transfer of accumulated volume from chamber 2 to chamber 31' will occur so long as accumulated volume of chamber 3 is not enough to drive its pressure up to p.
  • volume versus pressure functions for the accumulators shown in FIG. 2 have the characteristic that, for the largest pulse volume the system is ever designed to produce, VMAX, the maximum possible pressure of chamber 31', p MAX p MAX p MAX so that a pressure drop always exists between chambers l and 2 and between chamber 2 and any of the n chambers 3i. This pressure drop assures complete transfer of accumulated volumes between the accumulators toward the injection nozzles in the pressure cascading sequence.
  • This sequential transfer process of accumulated volume from higher pressure chamber to lower pressure chamber is complete and very fast, and does not depend (except at very fast speeds) on the exact values Ofpah p02, and p so long as p p p to assure that the transfer occurs over a pressure drop. It is a pressure drop cascade transfer process.
  • This transfer process between accumulator chambers connected in sequence by a rotary distributor is the es sence of the present invention.
  • Accumulator chambers 1 and 2 are in intermittent contact and chamber 2 is in intermittent sequential contact with the n accumulator chambers 31' which feed the n nozzles.
  • the pressure cascading transfer process filters the redundant metering cycle of the interaction of chambers 1 and 2 from any disturbing influences of variations between the various n injection lines and also assures that instantaneous flow velocities will be sufficient for atomization even under startup conditions, since the fuel flow pulses are produced by a sort of capacitive discharge technique.
  • FIG. 3 shows the fuel flow sequence of the injection system in a block diagram.
  • Rotary distributors l and 2 are rotated in synchrony (probably on a common shaft) so that accumulator 2 is open alternately to accumulator 1 and one of the accumulators 31'.
  • FIG. 4 shows the injection system flow pattern schematically.
  • Pressurized fuel from pressure source P is continuously metered through a flow control device comprising variable metering orifice V and diaphragm controlled bypass system 24, 5, 6 which maintains the average pressure drop across valve V at a constant value to assure accurate fuel metering at each setting of valve V.
  • the flow control device has a bypass system l0, 11 which short circuits flow above a set maximum pressure downstream of valve V. This bypass assures that metered volume per injection pulse cannot exceed a set value.
  • Accumulator chamber 2 is always open to the flow passage of distributor LI and L3 through always open distributor level 2 (L2), which is shaped so that the flow path between accumulators l, 2 and 3i does not vary from injection cycle to injection cycle.
  • chamber 2 comes in contact (in rotary sequence through distributor L3 from injection cycle to injection cycle) with one of the n accumulator chambers 31', and discharges all its accumulated volume into this chamber 31'. This process is always completed in the period of contact between chamber 2 and the chamber 3i.
  • the accumulated fuel in chamber 3i is maintained at sufficient pressure to cause nozzle ito discharge at a high rate.
  • the injection rate is reduced from this maximum rate and the fuel pulse is given the desired shape by the setting of needle valve 1' in line i, which is controlled along with other matching needle valves to control maximum injection rate as an increasing function of RPM (and perhaps other parameters).
  • the volume of chamber 2 after blowdown to the accumulator 3s does not change with variations in the pressures of the injection line chamber 3s (so long as p MAX is less than P the metering event, which is the result of the redundant interaction between the continuous fuel metering system and chambers 1 and 2, is substantially unaffected by dynamic variations and other variations between the various injection lines.
  • the only exception is due to the fact that the density of the fuel in chamber 2, as contact between ch2 and ch3i is closed, varies slightly with pressure because the bulk modulus of the fuel is not infinite. This effect is imperceptable in low pressure systems and is small even in ultrahigh pressure injection systems. Therefore, it is an excellent approximation to say that the metering of the system is unaffected by variations between the injection lines and nozzles. Metering accuracy does not, therefore, require that the flow characteristics of the lines and nozzles be closely matched.
  • FIG. 5 shows the flow pattern of the preferred form of rotary distributor.
  • the rotary distributor has three levels, a top level which opens and closes contact with chl eight times per revolution with the flow passage in rotor 12, a middle level which has an annular slot around it so that accumulator 2 is always in fluid contact with the chamber of 12 and which is shaped so that the flow path lengths between chamber 2 and any of the chamber 3s is equal, and on the bottom level a flow passage which places one of the accumulator chamber 3s in contact with the passage in rotor 12 whenever flow between the passage in rotor 12 is cut off from ch].
  • the three distributor levels are interconnected by a hole in the center of rotor 12.
  • Rotary distributors of the type shown in FIG. 5 have been successfully used in a number of injection systems employing rotary distributors.
  • the fuel flow pulse shape is important.
  • the ideal pulse has the characteristic that it injects a certain fuel flow per degree crank angle at all speeds with the pulse flow in the general shape of a square wave, quickly reaching its maximum flow rate, maintaining this rate throughout the injection, and then cutting off fuel flow sharply.
  • the present cascading injection pump device will not have these chracteristics unless it is modified with a pulse shaping means.
  • each of the n injection lines has a variable area needle valve in the line between accumulator 3i and nozzle i, and the n needle valves are linked so that each has its orifice opening equal to that of the others.
  • These needle valves are linked together through cog assembly 15 or some other linkage and are controlled with openings, an increasing function of RPM (control mechanism not shown).
  • nozzle i which is an outwardly opening pintle nozzle
  • fn k1 Pu-1 .11
  • prprpo the pressure drop across the nozzle
  • determining a nozzle flow rate means determining a nozzle pressure p,,.
  • the accumulator pressure of chamber 31' is always at least high enough for the maximum nozzle flow rate the system is designed to produce.
  • the needle valve throttles the fluid pressure of accumulator 3i down to the pressure p, to the desired flow rate (which is proportional to RPM).
  • the range of needle orifice opening a required in an injection system is pro portional to the flow range required times the square root of the desired range of needle valve pressure drops. For instance, if a constant maximum fuel flow rate per degree crank angle is required over a ten-fold RPM range (a lO-fold range of f") and the pressure drop range across the needle valve to attain that variation, given the variations of p and p is a 16-fold Ap range, a 40-fold variation of orifice area from maximum to minimum flow setting is required. Note that this 40:1 variation of a causes a 1600:] variation in the negative feedback coefficient of nozzle equilibrium k k /a In most practical cases the range of a required will be less than 40zl.
  • the interaction of the accumulator, needle valve, and injection nozzle will produce an excellent approximation of the desired square wave pulse characteristic.
  • the pulse shaping system is stable even at the highest operating speeds required.
  • FIG. 7 shows the equilibrium of injection rate f between an accumulator chamber, a needle valve in the line, and an outwardly opening pintle nozzle on the assumption that nozzle downstream pressure p and accumulator pressure p, are constant, to illustrate the function of the needle valve pulse shaping apparatus.
  • the needle valve pulse shaping technique will produce a bettern approximation to the ideal square wave injection characteristic than conventional injection pumps, because the system does not involve plungers with inertial mass or cam profiles which constrain the pulse shape.
  • FIG. 8 shows a continuous flow fuel metering system adapted to the injection system. Fuel is metered continuously through a metering valve V where the average pressure drop across the metering valve is held constant (as long as downstream pressure is below a set maximum) by a diaphragm controlled bypass valve assembly.
  • Fuel pressurized at pump P flows into line 21, where flow is divided between fuel flow to the engine through metering valve V or flow to a flow bypass through needle valve assembly 24.
  • Needle valve assembly 24 is opened and closed by diaphragm 5 which opens if the pressure in chamber la exceeds the pressure in chamber 1b plus the pressure of spring 6, and closes if pressure in chamber 1a is less than the pressure in lb plus spring 6s pressure, so that the average pressure drop across which metering valve V meters is maintained at a pressure drop corresponding to the force of spring 6.
  • Spring 6 is designed with a ratio of spring constant to actuating force such that its force on diaphragm 5 is nearly the same when bypass valve assembly 24 is fully open as when it is fully closed.
  • Chamber lb is connected with line 7 at the downstream pressure of valve V through porous plug 8.
  • Flow through plug 8 is quite restricted and quick pressure variations therefore cannot be transmitted ⁇ since pres sure transfer requires fluid flow: the fuel bulk modulus is not infinite).
  • Flow over the system pressure cycle through plug 8 serves to maintain chamber lb at the average (cycle average) pressure of line 7. Since the pressure in line 7 fluctuates quite rapidly with the opening and closing of accumulator l to accumulator 2, and since oscillation of the metering device would produce unacceptable cycle-to-cycle metering errors at the very high operating speeds required, the porous plugs function of suppressing servo-oscillation of the bypass system is important.
  • the system cannot be built so as to maintain a constant instantaneous pressure drop across valve V so the system is instead designed to maintain an average pressure drop very closely from cycle to cycle.
  • FIG. 8 can be modified in various ways to adapt it to requirements as, for instance, to adapt the system to very high injection pressure.
  • Diaphragm 5 can be replaced by a piston assembly to control the opening and closing of the bypass system: this adaptation of pressure compensated fluid metering systems is well known to the fluidic art and is particularly well adapted to very high pressure drops across metering valve V. High pressure drops are advantageous for certain systems, since it is important that the pressure drop across valve V should never change direction.
  • the pressure averaging effect of porous plug 8 could instead be severed by an orifice between line 7 and chamber 1b which are exceptionally small, to limit the maximum fluid transfer rate between chamber lb and line 7 and so serve to limit the rate of pressure equalization between the two chambers.
  • the metering accuracy of the device shown in FIG. 8, or of any pressure compensated metering device, will be diminished if the pressure in chamber la fluctuates out of phase with the injection metering events. It is best if the pressure upstream of'valve V is kept constant (over time periods of the order of a few cycles). This can be accomplished with a number of well known techniques such as placing a surge tank between pump P and valve V or by placing a properly chosen length of elastic tubing between the pump and the metering and bypass systems.
  • the elastic tubing technique has the advantage that it need accumulate less volume before achieving desired pressure changes.
  • continuous metering means may be substituted for the device of FIG. 8 to accomplish the continuous flow metering prior to the pressure drop cascade distribution system.
  • flow may be metered by some variable displacement pump.
  • a number of continuous fluid metering devices will serve the purpose of the device of FIG. 8, and the least expensive durable one is the best.
  • Chart 1 at the end of the drawings summarizes the design requirements and functions of the components of the injection system in tabular form. Note that the design tolerances of most of the components of the system are quite wide: the rotary distributor is the only component of the system which must be built to very close structural tolerances for sealing purposes. Note also that the component requirements of the system are very similar whether the system operates at an injection pressure of psi or 10,000 psi, and that the production cost difference between a high and a low pressure system is mainly due to the increasing 'cost of pumps with increasing pressures.
  • each of the working parts has a geometrically simple shape and a mathematically well defined function, that each parts function is simple,
  • Rotary fluid distributor Meters fuel across constant average pressure drop Ap. Fuel supplied to engine a unique function of valve setting over wide range of r.p.m.
  • Pump has pressurizing function but no metering function. Some pump leakage tolerable so long as pressure and volume adequate.
  • Porous plug suppresses oscillation. Want Ap spring to vary force little from full open to full close of bypass valve needle. Errors go as square root of Ap. Fluctuating pressures follow a redundant cycle.
  • Volumes must be invariant below accumulator pressures or cross-product errors due to variations between injection nozzle lines result. Volumes accumulated above meme must always be sufficient so pressure drop is never in the reverse of the cascading direction Chambers must accumulate very fast and discharge very fast (elastic tube type does this).
  • Componcnt(s) Function VI I... Pulse shaping needle valves in each injection line between the accumulator 3's and the nozzles (op- Comments Noodle valves controlled to open and close so restric- Generates desirable square wave typo pulse shape.
  • a timed, pulsed fuel injection system which injects fuel pulses through n nozzles in a repeating sequence comprising:
  • n 2 accumulator chambers (l, 2, 31, 32, 33,
  • each nozzle 1' is in continuous fluid connection with the corresponding accumulator chamber (31) (i l, 2,
  • first switching means to open and close fluid flow between the accumulator chambers l and 2) and a second switching means to open and close flow between accumulator chamber (2) in succession to accumulator chamber (31,32, 33, 3n); where said first and second switching means open and close fluid contact between the accumulator chambers in the sequence (l-2, 2-31, 1-2, 2-32, l-2, 2-33, 1-2, 2-31-2, 2, 2-31, l-2, and
  • each accumulator chamber i has a volume versus pressure function V, (P such that dV /dP if pressure P, in the chamber 1' is less than a set pressure P,,,, where d V, is large if P, P,,,, and where the accumulator pressures P for each chamber 1' are related so that P,,, P,,, P,,;,, or F or P or or P 2.
  • each accumulator comprises a composite tube including a section of rigid tubing having holes distributed therein, a resilient tube fitting closely over the rigid tubing, and sealing means on each end of the composite tube to provide a'seal betwcenthc rigid tube and the resilient tube positioned thereover.
  • variable orifices in the flow path between the accumulator chambers-(3i) and the nozzles i l, 2, 3, n) where each of said variable orifices has an opening controlled in response to RPM to adjust the maximum first and second switching means are in the form of a rotary distributor opening and closing fluid contact between the accumulator chambers in the sequence (l-2,
  • the means to meter pressurized fluid flow continuously to accumulator chamber includes: a source of pressurizedffuel; a bypass valve to a bypass line; a valve; fluid chamber connecting said source of pressure to said bypass valve and said. metering valve; a feed line to accumulator chamber (1) downstream of said metering valve; a take-off from said feed line; pressure responsive means to open said bypass valve when the pressure difference between said take-off and said chamber exceeds a certain value and to close said bypass valve when the pressure difference between said takeoff and said chamber is less than a certain value, to maintain a constant pressure drop between said take-off and said chamber.
  • said maximum pressure control 'mcans is a spring loaded bypass valve which opens a pressure relief line to release volume from a chamber when the pressure in said chamber exceeds a specified value.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
US05339153 1973-03-08 1973-03-08 Timed pulsed fuel injection apparatus and method Expired - Lifetime US3810581A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US05339153 US3810581A (en) 1973-03-08 1973-03-08 Timed pulsed fuel injection apparatus and method
GB965074A GB1469164A (en) 1973-03-08 1974-03-04 Timed pulsed fuel injection apparatus and method
CA194,046A CA1016433A (en) 1973-03-08 1974-03-05 Timed, pulsed fuel injection apparatus and method
SE7402966A SE404235B (sv) 1973-03-08 1974-03-06 Styrd pulserande brensleinjektor for forbrenningsmotorer
FR7407842A FR2220677B3 (it) 1973-03-08 1974-03-07
JP49026423A JPS6035545B2 (ja) 1973-03-08 1974-03-08 定時パルス燃料噴射装置
DE19742411787 DE2411787C3 (de) 1973-03-08 1974-03-08 Brennstoff-Einspritzeinrichtung für Brennkraftmaschinen
IT2874174A IT1019575B (it) 1973-03-08 1974-04-08 Apparecchio sincronizzato per iniezione pulsante di carburante

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US05339153 US3810581A (en) 1973-03-08 1973-03-08 Timed pulsed fuel injection apparatus and method

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US43348174A Division 1974-01-15 1974-01-15

Publications (1)

Publication Number Publication Date
US3810581A true US3810581A (en) 1974-05-14

Family

ID=23327742

Family Applications (1)

Application Number Title Priority Date Filing Date
US05339153 Expired - Lifetime US3810581A (en) 1973-03-08 1973-03-08 Timed pulsed fuel injection apparatus and method

Country Status (7)

Country Link
US (1) US3810581A (it)
JP (1) JPS6035545B2 (it)
CA (1) CA1016433A (it)
FR (1) FR2220677B3 (it)
GB (1) GB1469164A (it)
IT (1) IT1019575B (it)
SE (1) SE404235B (it)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3891151A (en) * 1974-05-01 1975-06-24 Merle Robert Showalter Pilot injection fuel injection pump
US4440134A (en) * 1981-05-15 1984-04-03 Kabushiki Kaisha Komatsu Seisakusho Fuel injection system for internal combustion engines
US4778107A (en) * 1986-08-21 1988-10-18 Nippondenso Co., Ltd. Fuel injection valve assembly and an assembling method therefor
US5887569A (en) * 1997-07-17 1999-03-30 Pacer Industries, Inc. Centrifugal fuel distributor
US6401691B1 (en) * 1998-10-22 2002-06-11 Nippon Soken, Inc. Fuel supply system for relieving fuel pressure pulsations and designing method thereof
US6460511B2 (en) * 1998-05-13 2002-10-08 Sanshin Kogyo Kabushiki Kaisha Fuel supply for direct injected engine
US7004146B1 (en) * 1999-08-24 2006-02-28 Sanshin Kogyo Kabushiki Kaisha Fuel injection system for outboard motor
US20060137656A1 (en) * 2003-11-25 2006-06-29 Zdroik Michael J Fuel rail crossover hose
US11035331B2 (en) * 2018-01-31 2021-06-15 Jonathan Tom Tavernier Internal combustion engine with tubular fuel injection

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3077872A (en) * 1961-07-17 1963-02-19 Georgia Tech Res Inst Fuel injection system
US3752136A (en) * 1970-07-10 1973-08-14 Cav Ltd Liquid fuel injection pumping apparatus

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3077872A (en) * 1961-07-17 1963-02-19 Georgia Tech Res Inst Fuel injection system
US3752136A (en) * 1970-07-10 1973-08-14 Cav Ltd Liquid fuel injection pumping apparatus

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3891151A (en) * 1974-05-01 1975-06-24 Merle Robert Showalter Pilot injection fuel injection pump
US4440134A (en) * 1981-05-15 1984-04-03 Kabushiki Kaisha Komatsu Seisakusho Fuel injection system for internal combustion engines
US4778107A (en) * 1986-08-21 1988-10-18 Nippondenso Co., Ltd. Fuel injection valve assembly and an assembling method therefor
US5887569A (en) * 1997-07-17 1999-03-30 Pacer Industries, Inc. Centrifugal fuel distributor
US6460511B2 (en) * 1998-05-13 2002-10-08 Sanshin Kogyo Kabushiki Kaisha Fuel supply for direct injected engine
US6401691B1 (en) * 1998-10-22 2002-06-11 Nippon Soken, Inc. Fuel supply system for relieving fuel pressure pulsations and designing method thereof
US7004146B1 (en) * 1999-08-24 2006-02-28 Sanshin Kogyo Kabushiki Kaisha Fuel injection system for outboard motor
US20060137656A1 (en) * 2003-11-25 2006-06-29 Zdroik Michael J Fuel rail crossover hose
US7143748B2 (en) * 2003-11-25 2006-12-05 Millennium Industries, Corp. Fuel rail crossover hose
US11035331B2 (en) * 2018-01-31 2021-06-15 Jonathan Tom Tavernier Internal combustion engine with tubular fuel injection

Also Published As

Publication number Publication date
SE404235B (sv) 1978-09-25
DE2411787B2 (de) 1977-03-31
JPS6035545B2 (ja) 1985-08-15
CA1016433A (en) 1977-08-30
JPS5040928A (it) 1975-04-15
IT1019575B (it) 1977-11-30
DE2411787A1 (de) 1974-09-26
FR2220677B3 (it) 1976-12-17
FR2220677A1 (it) 1974-10-04
GB1469164A (en) 1977-03-30

Similar Documents

Publication Publication Date Title
US3810581A (en) Timed pulsed fuel injection apparatus and method
SU518155A4 (ru) Система впрыска топлива в двигатель внутреннего сгорани
US3946714A (en) Fuel injection system
US3425403A (en) Injection pump arrangement for combustion engine
US3980093A (en) Timed pulsed fuel injection apparatus and method
US4138981A (en) Fuel injection pumping apparatus for internal combustion engines
US3820517A (en) Fuel injection system
US2899948A (en) groves
US2319566A (en) Fuel pump
US3891151A (en) Pilot injection fuel injection pump
ES315188A1 (es) Perfeccionamientos en los sistemas de inyecciën continua de combustible a baja presiën para motores de combustiën interna
US4200074A (en) Fuel injection system for an internal combustion engine
US4132205A (en) Metering valve for fuel injection
US3687121A (en) Fuel system
US3327632A (en) Variable stroke dual plunger pump
GB1487178A (en) Fuel injection pumping apparatus
US3794005A (en) Fluidic fuel injection system utilizing simplified fluidic computation element
EP0607982A1 (en) Infinitely variable hydromechanical timing control
US3079948A (en) Variable volume fluid distributor
US3238934A (en) Liquid-fuel distributing means for internal combustion engines
US2851025A (en) Fuel injector mechanism
US3481315A (en) Liquid fuel supply systems for internal combustion engines
GB1472125A (en) Fuel-injection pump for an internal combustion eingine
US2102485A (en) Fuel injection means for motors
US2902989A (en) Charge forming means

Legal Events

Date Code Title Description
AS Assignment

Owner name: AUTOMOTIVE ENGINE ASSOCIATES, 301 S. BLOUNT ST., C

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:SHOWALTER, MERLE R.;RHINE, SAMUEL;REEL/FRAME:004261/0788;SIGNING DATES FROM 19800131 TO 19800710

AS Assignment

Owner name: ANATECH, 2102 IRIS LANE, MADISON, WI., 53711, A CO

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:AUTOMOTIVE ENGINE ASSOCIATES, A LIMITED PARTNERSHIP OF WI., BY JAMES W. MYRLAND;REEL/FRAME:004724/0602

Effective date: 19870505