US3678907A - Engine spark timing system - Google Patents

Engine spark timing system Download PDF

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Publication number
US3678907A
US3678907A US59500A US3678907DA US3678907A US 3678907 A US3678907 A US 3678907A US 59500 A US59500 A US 59500A US 3678907D A US3678907D A US 3678907DA US 3678907 A US3678907 A US 3678907A
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United States
Prior art keywords
spark
flow
servo
vacuum
port
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Expired - Lifetime
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US59500A
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English (en)
Inventor
Richard D Vartanian
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Ford Motor Co
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Ford Motor Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
    • F02P5/00—Advancing or retarding ignition; Control therefor
    • F02P5/04—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions
    • F02P5/05—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means
    • F02P5/10—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means dependent on fluid pressure in engine, e.g. combustion-air pressure
    • F02P5/103—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means dependent on fluid pressure in engine, e.g. combustion-air pressure dependent on the combustion-air pressure in engine

Definitions

  • it relates to an apparatus that provides good operating performance as well as good fuel economy by not only quickly lowering the spark timing advance setting upon rapid vehicle accelerations, but also providing a rapid return to essentially the former setting upon momentary decelerations and return of the engine towards its former condition of operation.
  • the latter shows a mechanical device in the vacuum line between a carburetor spark port and a vacuum servo to control the movement of the distributor breaker plate to advance or retard the engine spark timing setting.
  • the device includes a one-way check valve and an orifice in parallel flow circuits. During rapid vehicle accelerations, the check valve unseats to provide a quick equalization of the pressure at the servo to the spark port vacuum, thereby lowering the spark advance setting to avoid detonation.
  • the orifice Upon a momentary deceleration condition of operation, with a subsequent return towards its former operating condition, the orifice provides a slow buildup of the vacuum level at the servo to equal that at the spark port so that the advance setting only slowly returns to normal. This results in lower peak combustion temperatures and pressures and less emission of engine pollutants.
  • This invention provides all of the advantageous functions described, plus a rapid return of the spark timing advance setting to essentially its former level, after a momentary deceleration, to improve the fuel economy.
  • the invention includes in the vacuum line between the carburetor spark port and distributor servo a first one-way check valve in parallel flow relationship with a vacuum reservoir or accumulator.
  • the reservoir is open at one end to the carburetor spark port and at its opposite end to the distributor servo line, and contains adjacent each end an orifice or flow restricting control.
  • the flow restriction adjacent the spark port end of the reservoir is located in the opening of a second one-way check valve that operates in a direction opposite to that of the first one-way check valve previously described.
  • the above construction permits a quick equalization of the spark port and servo port pressure levels during rapid vehicle accelerations by unseating of the first or main check valve. It also simultaneously seats the reservoir one-way check valve to seal off the bleed of vacuum from the reservoir to the spark port end while allowing only slow leakage of vacuum through the other end and through the open parallel flow check valve. Upon a momentary deceleration and subsequent reacceleration towards its previous condition of operation, the main check valve seats or closes, and the vacuum of the reservoir quickly returns the distributor servo port pressure to the reservoir level. This generally is close to or essentially the level that existed prior to vehicle rapid acceleration depending upon the duration of the deceleration.
  • FIG. 1 schematically illustrates a partial cross sectional view of an engine spark timing system embodying the invention.
  • FIG. 2 graphically illustrates different operating conditions of the spark timing system shown in FIG. 1.
  • FIG. 1 shows, schematically, only those portions of an internal combustion engine that are normally associated with the engine distributor spark timing setting control; such as, for example, a carburetor 10, a distributor breaker plate 12, a vacuum servo 14 to control the movement of breaker plate 12, and a line 16 connected between the carburetor and vacuum servo to automatically change the engine spark timing setting as a function of changes in engine vacuum spark port setting.
  • a carburetor 10 to control the movement of breaker plate 12
  • a vacuum servo 14 to control the movement of breaker plate 12
  • line 16 connected between the carburetor and vacuum servo to automatically change the engine spark timing setting as a function of changes in engine vacuum spark port setting.
  • carburetor 10 is shown as being of the downdraft type having the usual air-fuel induction passage 18 with an atmospheric air inlet 20 at one end and connected to the engine intake manifold 22 at the opposite end.
  • Passage 18 contains the usual fixed area venturi 24 and a throttle valve 26. The latter is rotatably mounted on a part ofthe carburetor body across passage 18 in a manner to control the flow of airfuel mixture into the intake manifold.
  • Fuel would be inducted in the usual manner from a nozzle, not shown, projecting into or adjacent venturi 24, in a known manner.
  • Throttle valve 26 is shown in its engine idle speed position essentially closing induction passage 18, and is rotatable to a nearly vertical position essentially unblocking passage 18.
  • a spark port 28 is provided at a point just above the idle position of throttle valve 26, to be traversed by the throttle valve during its opening or part throttle movements. This will change the vacuum level in spark port 28 as a function of the rotative position of the throttle valve, the spark port reflecting essentially atmospheric pressure in the air inlet 20 upon closure of the throttle valve.
  • the distributor includes a breaker plate 12 that is pivotally mounted at 30 on a stationary portion of the distributor, and movable with respect to cam 32.
  • the latter has six peaks 34 corresponding to the number of engine cylinders. Each of the peaks cooperates with the follower 36 of a breaker point set 38 to make and break the spark connection in a known manner for each one-sixth, in this case, rotation of cam 32.
  • Pivotal movement of breaker plate 12 in a counterclockwise spark retard setting direction, or in a clockwise spark advance setting is provided by an actuator 40 slidably extending from vacuum servo l4.
  • Servo 14 may be of a conventional construction. It has a hollow housing 42 whose interior is divided into an atmospheric pressure chamber 44 and a vacuum chamber 46 by an annular flexible diaphragm 48. The diaphragm is fixedly secured to actuator 40, and is biased in a rightward retard direction by a compression spring 50. Chamber 44 has an atmospheric or ambient pressure vent, not shown, while the chamber 46 is connected by a bore 52 to line 16.
  • the vacuum line 16 consists of two branches 54 and 56 in parallel flow relationship.
  • the branch 54 which may be termed the main branch, contains a conventional one-way check valve 58 having the usual spring pressed ball or other similar device 60 unidirectional in operation. That is, communication between the spark port 28 and servo chamber 46 is usually prevented through line 54 by the seating of ball valve 60 when the pressure level at the spark port is less than that at the servo chamber 46. This, of course, will occur during normal acceleration modes of operation when the intake manifold vacuum is increasing to gradually lower the servo vacuum in chamber 46 and advance the breaker plate 12.
  • a branch line 56 contains a vacuum reservoir or accumulator 62 consisting of a cylindrical or suitable receptacle having ports 64 and 66 at opposite end connected respectively to the carburetor spark port 28 and distributor servo chamber 46. Adjacent port 66, the reservoir contains an orifice or flow restricting member 68 to provide slow communication of the pressure levels between port 66 and the chamber 70 defined within reservoir 62. The size of the orifice 68, of course, will be chosen to provide the desired delay, in a manner to be described.
  • a partition member 72 Adjacent the opposite end of reservoir 62 is a partition member 72 having a central aperture 74 closed by a unidirectional or one-way check valve 76.
  • the latter consists of a flapper or umbrella type seal having a flexible membrane 78 secured on an axial stem 80.
  • the stem projects through the central bore 74 and is surrounded by a sintered metal type disc or plug orifice 82.
  • the sintered plug 82 consists of randomly oriented and dispersed multitudes of minute metal particles that are bonded together to form labyrinthian type fluid passa'gesconnecting the voids between particles.
  • a pressure level at the carburetor spark port 28, such as during coasting, higher than the level in reservoir 70 will seat check valve 76 and prevent bleed-off of vacuum into the carburetor spark port opening.
  • a lower vacuum in carburetor spark port 28 will unseat check valve 76 and permit only slow equalization of pressure levels between carburetor spark port 28 and reservoir chamber 70, and servo chamber 46 through orifice 68.
  • the total decay in vacuum at the servo chamber 46 will be less than for a closed throttle decel condition, with a resultant less of a reduced setting of the distributor breaker plate.
  • the former condition is represented graphically in FIG. 2 by the line BD showing the decay in spark port vacuum.
  • main check valve 58 will again close. During this brief interval, the vacuum in reservoir chamber 70 will bleed slowly through orifice 68 into the open line 54b past the open check valve 58. This is represented by the curve BE in FIG. 2, and will move along the curve BC as a function of the length of time of the decel condition, i.e., the length of time that the throttle is maintained in the decel position. As soon as main check valve 58 closes, the continuing bleed of vacuum from chamber 70 through orifice 68 and line 54b will again permit opening of check valve 58 to maintain servo chamber 46 at the pressure level at the spark port. Therefore, the check valve 58 will oscillate or essentially be maintained in an equilibrium position maintaining the servo chamber 46 at the pressure level of the spark port with a continuing slow decay in the vacuum reservoir chamber 70. This slow decay will essentially follow the curve BC in FIG. 2.
  • the carburetor spark port vacuum has decayed as indicated by the line BD.
  • the reservoir vacuum in chamber 70 has decayed along the line BC to BE, and the rapid recovery of the spark setting is along the E to F.
  • Point E indicates the point at which the breaker plate setting is located immediately upon shutting of check valve 58 upon reacceleration of the engine.
  • the line EF represents the time interval it takes for the vacuum level in the induction passage to build up to its formal level. If it were not for the reservoir and orifice 68, the normal build up of vacuum would be delayed by orifices 82 and 68 to follow the curve GH.
  • the line AB illustrates the slow buildup of vacuum at the distributor servo by means of the orifices 82 and 68.
  • the line BD represents the quick decay in spark port vacuum to essential atmospheric pressure upon return of the throttle valve to an idle speed position, the reservoir vacuum at this time decaying slowly through the closed check I valve 76 and the orifice 68 along the line BC.
  • opening of the throttle valve raises the vacuum level at the spark port to a point above the reservoir vacuum so that main check valve 58 seats at point B and the higher vacuum at the spark port is slowly communicated through the open check valve 76 and sintered orifice 82 and orifice 68 into servo chamber 46 to move the breaker plate back to a maximum advance setting.
  • the curve GH in FIG. 2 would represent the condition of recovery of the vacuum at the servo were it not for the reservoir chamber 70, since then there would only be a slow buildup of the vacuum at the spark port through the orifice 82.
  • HO. 2 also represents the various conditions of operation if only certain portions of the control of FIG. 1 were used.
  • a system with orifice 82 only is represented by curve A to B during acceleration and curve B to C during deceleration. Delay time for acceleration and deceleration are equal. This system would be unsatisfactory during fast acceleration from constant speeds that have full spark advance since the engine requires a lower spark advance at this time. Not capable of achieving this, spark knock would result.
  • a system with orifice 82 and main check valve 58 corrects spark knock problem described above.
  • the check valve 58 equalizes the vacuum at the distributor vacuum chamber 46 to the spark port vacuum.
  • the invention provides for normal spark advance by slow buildup in vacuum in the reservoir chamber 70 through the sintered metal orifice 82 so that lower peak combustion temperatures and pressures are obtained resulting in less exhaust emission of pollutants. It will also be seen that for engine performance, opening of check valve 58 immediately equalizes the servo pressure level to that at the spark port and thereby reduces the advance setting of the distributor to prevent spark detonation.
  • a spark timing control system comprising, an engine carburetor having an induction passage containing a spark port located above the idle speed position of a throttle valve controlling flow through the passage and subject to the change in pressure level in the carburetor as a function of the movement of the throttle valve from its idle speed position, an engine distributor having a breaker plate pivotally movable in opposite directions to advance and retard the spark timing, vacuum controlled servo means connected to said breaker plate for moving the same, conduit means connecting said spark port and servo means, and slow-fast flow rate control means in said conduit means to control the rate of change of application of vacuum from said spark port to said servo means, said control means including faster flow rate means operable in response to a change in the vacuum at said spark port to a lesser pressure depression than at said servo means to quickly equalize the pressure level at said servo means to that at the spark port, and slower flow rate means in a fluid flow circuit bypassing said faster flow rate means, said slower flow rate means including a fluid reservoir open at one end to said spark port and open
  • said faster flow rate control means comprising a one-way check valve permitting flow in a direction from the spark port to the servo means only.
  • said slower rate flow restricting means comprising an orifice adjacent one end of said reservoir and a one-way check valve at the opposite end.
  • said one-way check valve having a restricted flow area in its open flow condition of operation.
  • said faster rate flow means comprising a one-way check valve operable in a direction opposite to that of said slower flow rate one-way check valve means.
  • a spark timing control system comprising, an engine carburetor having an induction passage containing a spark port located above the idle speed position of a throttle valve controlling fiow through the passage and subject to the change in vacuum in the induction passage as a function of the movement of the throttle valve from its idle speed position, an engine distributor having a breaker plate pivotally movable in opposite directions to advance and retard the spark timing, vacuum controlled servo means connected to said breaker plate for moving the same, conduit means connecting said spark port and servo means, and slowfast flow rate control means in said conduit means to control the rate of change of application of vacuum from said spark port to said servo means, said control means including slower rate flow restricting means in the conduit means delaying communication of lower pressure levels at the spark port to the servo means, fast rate open-close flow means operably movable to an open position upon the attainment of a higher pressure level at said spark port than at said servo means to immediately equalize the pressure levels and reduce the spark timing setting, and further means operable at times to override the action of

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Ignition Installations For Internal Combustion Engines (AREA)
  • Electrical Control Of Ignition Timing (AREA)
US59500A 1970-07-30 1970-07-30 Engine spark timing system Expired - Lifetime US3678907A (en)

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Application Number Priority Date Filing Date Title
US5950070A 1970-07-30 1970-07-30

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US3678907A true US3678907A (en) 1972-07-25

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US59500A Expired - Lifetime US3678907A (en) 1970-07-30 1970-07-30 Engine spark timing system

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US (1) US3678907A (enrdf_load_stackoverflow)
JP (1) JPS5037816B1 (enrdf_load_stackoverflow)
CA (1) CA947159A (enrdf_load_stackoverflow)
DE (1) DE2134901C2 (enrdf_load_stackoverflow)
GB (1) GB1303931A (enrdf_load_stackoverflow)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3857373A (en) * 1972-12-01 1974-12-31 Chrysler Corp Vacuum delay valve
US3902469A (en) * 1973-11-07 1975-09-02 Stp Corp Vacuum delay valve
US3911880A (en) * 1973-10-30 1975-10-14 Ford Motor Co Spark delay device for internal combustion engine ignition timing
US3920041A (en) * 1973-11-05 1975-11-18 Ford Motor Co Fluid flow control device
US4010721A (en) * 1975-04-24 1977-03-08 The Bendix Corporation Vacuum delay/relief valve
US4031869A (en) * 1974-02-18 1977-06-28 Toyota Jidosha Kogyo Kabushiki Kaisha Ignition-timing adjusting system for spark-ignition internal combustion engines
US4098850A (en) * 1974-09-04 1978-07-04 Aisin Seiki Kabushiki Kaisha Orifice device for air flow restriction
US4112888A (en) * 1975-12-26 1978-09-12 Toyota Jidosha Kogyo Kabushiki Kaisha Ignition timing controller for a gasoline engine
US4126084A (en) * 1973-10-11 1978-11-21 Masami Inada Ignition time adjuster for an internal combustion engine
US4151818A (en) * 1974-11-06 1979-05-01 Toyota Jidosha Kogyo Kabushiki Kaisha Ignition timing adjusting system for spark-ignition internal combustion engines
US20210324969A1 (en) * 2017-03-30 2021-10-21 Donaldson Company, Inc. Vent with relief valve

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5217639Y2 (enrdf_load_stackoverflow) * 1974-08-08 1977-04-21
JPS5352909A (en) * 1976-10-22 1978-05-13 Mitsubishi Electric Corp Controller for starting induction motor

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2377566A (en) * 1943-11-19 1945-06-05 Mallory Marion Ignition timing control means for internal-combustion engines
US2392680A (en) * 1944-12-13 1946-01-08 Mallory Marion Pressure ignition system for internal-combustion engines
US2650581A (en) * 1949-11-03 1953-09-01 Gen Motors Corp Ignition apparatus
US3157168A (en) * 1961-01-18 1964-11-17 Holley Carburetor Co Spark control valve for ignition distributors
US3472213A (en) * 1967-06-22 1969-10-14 Brooks Walker Spark timing control

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3131681A (en) * 1962-03-09 1964-05-05 Ford Motor Co Spark advance system
US3638626A (en) * 1970-07-06 1972-02-01 Ford Motor Co Engine spark timing control device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2377566A (en) * 1943-11-19 1945-06-05 Mallory Marion Ignition timing control means for internal-combustion engines
US2392680A (en) * 1944-12-13 1946-01-08 Mallory Marion Pressure ignition system for internal-combustion engines
US2650581A (en) * 1949-11-03 1953-09-01 Gen Motors Corp Ignition apparatus
US3157168A (en) * 1961-01-18 1964-11-17 Holley Carburetor Co Spark control valve for ignition distributors
US3472213A (en) * 1967-06-22 1969-10-14 Brooks Walker Spark timing control

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3857373A (en) * 1972-12-01 1974-12-31 Chrysler Corp Vacuum delay valve
US4126084A (en) * 1973-10-11 1978-11-21 Masami Inada Ignition time adjuster for an internal combustion engine
US3911880A (en) * 1973-10-30 1975-10-14 Ford Motor Co Spark delay device for internal combustion engine ignition timing
US3920041A (en) * 1973-11-05 1975-11-18 Ford Motor Co Fluid flow control device
US3902469A (en) * 1973-11-07 1975-09-02 Stp Corp Vacuum delay valve
US4031869A (en) * 1974-02-18 1977-06-28 Toyota Jidosha Kogyo Kabushiki Kaisha Ignition-timing adjusting system for spark-ignition internal combustion engines
US4098850A (en) * 1974-09-04 1978-07-04 Aisin Seiki Kabushiki Kaisha Orifice device for air flow restriction
US4151818A (en) * 1974-11-06 1979-05-01 Toyota Jidosha Kogyo Kabushiki Kaisha Ignition timing adjusting system for spark-ignition internal combustion engines
US4010721A (en) * 1975-04-24 1977-03-08 The Bendix Corporation Vacuum delay/relief valve
US4112888A (en) * 1975-12-26 1978-09-12 Toyota Jidosha Kogyo Kabushiki Kaisha Ignition timing controller for a gasoline engine
US20210324969A1 (en) * 2017-03-30 2021-10-21 Donaldson Company, Inc. Vent with relief valve
US11692644B2 (en) * 2017-03-30 2023-07-04 Donaldson Company, Inc. Vent with relief valve
US12078265B2 (en) 2017-03-30 2024-09-03 Donaldson Company, Inc. Vent with relief valve

Also Published As

Publication number Publication date
CA947159A (en) 1974-05-14
DE2134901C2 (de) 1982-12-16
GB1303931A (enrdf_load_stackoverflow) 1973-01-24
DE2134901A1 (de) 1972-02-03
JPS5037816B1 (enrdf_load_stackoverflow) 1975-12-05

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