US3698366A - Engine spark timing control system - Google Patents

Engine spark timing control system Download PDF

Info

Publication number
US3698366A
US3698366A US60489A US3698366DA US3698366A US 3698366 A US3698366 A US 3698366A US 60489 A US60489 A US 60489A US 3698366D A US3698366D A US 3698366DA US 3698366 A US3698366 A US 3698366A
Authority
US
United States
Prior art keywords
vacuum
spark
servo
port
branch
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
US60489A
Other languages
English (en)
Inventor
Karl H Gropp
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.)
Ford Motor Co
Original Assignee
Ford Motor Co
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 Ford Motor Co filed Critical Ford Motor Co
Application granted granted Critical
Publication of US3698366A publication Critical patent/US3698366A/en
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
    • 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

  • ABSTRACT A mechanical device is located between the carburetor spark and intake manifold vacuum Mich.
  • This invention relates, in general, to an engine spark timing control system. More particularly, it relates to an apparatus that provides good operating performance as well as 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 mementary decelerations and return of the engine towards its former condition of operation.
  • 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 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 a vacuum line between an intake manifold port and the distributor servo a spring operated, vacuum controlled valve in parallel flow relationship with a flow restriction in the vacuum line between the carburetor spark port and the distributor servo line.
  • the above construction permits a quick lowering of the servo port pressure level during rapid vehicle accelerations by unseating of the valve in response to lowered manifold vacuums. It also permits a rapid recovery of the spark timing advance setting upon a momentary deceleration and subsequent reacceleration towards its previous condition of operation, from a light acceleration mode of operation; the high manifold vacuum seats the valve, and the distributor servo vacuum decays only slowly through the orifice. Therefore, upon light reacceleration, the servo port pressure is near the previous level. This generally is close to or essentially the level that existed prior to the original vehicle 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. l shows, schematically, only those portions of an internal combustion engine that are normally associated with the enginedistributor' 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 a distributor 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 I0 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 of the carburetor body across passage 18 in a manner to control the flow of airfuel mixture into the intake manifold.
  • Fuel would be in ducted 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 part throttle opening 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.
  • An intake manifold vacuum sensing port 30 is also provided, for a purpose to be described.
  • the distributor includes a breaker plate 12 that is pivotallymounted at 31 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 or 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 14.
  • 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 diaphragmis 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, not shown, to line 16.
  • the vacuum line 16 consists of two branches S4 and 56 in parallel flow relationship.
  • the branch 54 is adapted to be blocked or unblocked by a movable power operated valve 58.
  • the latter is operatively fixed to the annular flexible diaphragm 60 of a vacuum controlled servo 62.
  • the servo is essentially conventional, and includes a hollow housing divided by the diaphragm 60 into an atmospheric or ambient pressure chamber 64, and a vacuum chamber 66.
  • Chamber 64 is connected to atmosphere by a hole 68, while chamber 66 is connected to intake manifold sensing port 30 by a passage 70.
  • a spring 72 normally biases diaphragm 60 and valve 58 off its seat 74.
  • the sintered orifice 78 is constructed of randomly oriented and dispersed multitudes of minute metal particles that are bonded together to form labyrinthian type fluid passages connecting the voids between particles.
  • valve 58 an intake manifold vacuum force in line 70 higher than the force of spring 72 will seat valve 58 and cause the changes in the breaker plate setting to be made only slowly via orifice 78, as a function of light acceleration changes and decelerations by means of throttle valve 26.
  • a lower manifold vacuum force will effect unseating of valve 58 and permit a quick equalization of the pressure levels between the manifold and servo chamber 46, to quickly lower the advance setting to avoid detonation.
  • the servo chambers 44 and 46, and 64 and 66 are equalized and essentially at atmospheric pressure.
  • the diaphragm 60 and valve 58 are held away from the seat 74 by the spring 72, and passage 70 thereby completes a circuit from the intake manifold to the servo chamber 46 through passages 54 and 16.
  • the intake vacuum at the manifold 22 is at a high level, and continues to keep the diaphragm 60 and valve 58 on its seat.
  • the spark port 28 is exposed to an essentially atmospheric pressure.
  • the flow of air, which destroys the distributor servo chamber 46 advance signal, is then controlled by the metering restriction 7 8. This in turn allows for a gradual reduction of spark advance.
  • the controlled decay of the spark advance signal offers yet another advantage.
  • the spark advance signal has only been'partially destroyed.
  • the high intake manifold vacuum has. maintained valve 58 seated so the decay of vacuum in servo chamber 46 can occur only slowly through orifice 78. Then, on a light reacceleration, the spark signal will still be near the desired position for this particular speed and load. This minimizes depreciation of fuel economy.
  • FIG. 2 represents the various operations of the invention.
  • the line AB illustrates the slow buildup of vacuum at the distributor servo by means of the orifice 78 and seating of valve 58.
  • the line BD represents the quick decay in distributor servo chamber 46 vacuum to essential atmospheric pressure upon unseating of valve 58 during rapid vehicle accelerations to quickly lower the advance setting.
  • Line GH represents the slow return to advance setting upon gradual release of the accelerator pedal from the rapid condition. Of course, this line will move up as a function of the degree of depression of the accelerator pedal during rapid accelerator pedal during rapid accelerations.
  • Line BC represents the slow I decay in advance chamber 46 vacuum during vehicle decelerations.
  • the high manifold vacuum seats valve 58 and allows decay only slowly through orifice 78. if reacceleration occurs before a total decay in vacuum, such as at point E, the advance setting quickly returns to its former setting, at point F.
  • 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 depression 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, an engine manifold vacuum port, first vacuum controlled servo means connected to said breaker plate for moving the same, slowfast flow rate control means between said spark port and servo means to control the rate of change of application of vacuum from said spark port to said servo means, said control means including flow restriction means operable in response to light accelerations indicated by gradual vacuum level increases at said spark port occasioned by gradual throttle valve openings for slowly applying the vacuum increase to said servo means to slowly advance the engine spark timing, said flow restriction means also being operable in response to engine deceleration conditions indicated by a decaying vacuum level at said spark port occasioned by closing throttle movements for delaying the decay of
  • said second vacuum controlled means comprising a second vacuum servo means having a flexible diaphragm dividing said latter servo means into a chamber connected to atmospheric pressure and a chamber interposed in said second branch connected at one portion to said intake manifold port and at another portion to said first servo means, said diaphragm in a first position operatively blocking said second branch in response to intake IEaIIifOIdVgCULIm above a predetermined level acting t ereon, w ereby the change in rate of application 0 vacuum to said distributor servo means is controlled by said orifice, and-spring means biasing said diaphragm to a second position unblocking said second branch.
  • said second vacuum controlled means including a valve movable in said second branch between a flow blocking position in response to intake manifold vacuum above a predetermined level operatively acting thereon and a position unblocking said second branch, and spring means for moving said valve to said flow unblocking position.
  • said second vacuum controlled means including a second vacuum servo having a power actuated member connected to said valve and actuated in response to changes in said intake manifold vacuum.
  • 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 depression 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, an engine manifold vacuum port, first vacuum controlled servo means connected to said breaker plate for moving the same, slowfast flow rate control means between said ports and servo means to control the rate of change of application of vacuum from said spark.
  • said control means including conduit means connecting said manifold vacuum port and said spark port in branch parallel flow paths to said servo means, said spark port branch containing an orifice delaying the application of the change of pressure level at said spark port to said servo means, said manifold vacuum branch containing a servo operated valve blocking said manifold vacuum branch at higher manifold vacuums above a predetermined level so that changes in engine spark timing are controlled by the time delay of said orifice, said valve at lower manifold vacuums operatively unblocking said manifold vacuum branch to rapidly equalize the first servo means pressure level to the intake manifold vacuum level whereby said spark timing setting is rapidly lowered.

Landscapes

  • 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)
  • Electrical Control Of Ignition Timing (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
US60489A 1970-08-03 1970-08-03 Engine spark timing control system Expired - Lifetime US3698366A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US6048970A 1970-08-03 1970-08-03

Publications (1)

Publication Number Publication Date
US3698366A true US3698366A (en) 1972-10-17

Family

ID=22029809

Family Applications (1)

Application Number Title Priority Date Filing Date
US60489A Expired - Lifetime US3698366A (en) 1970-08-03 1970-08-03 Engine spark timing control system

Country Status (6)

Country Link
US (1) US3698366A (show.php)
JP (1) JPS5037817B1 (show.php)
CA (1) CA947158A (show.php)
DE (1) DE2137234C3 (show.php)
FR (1) FR2103892A5 (show.php)
GB (1) GB1293713A (show.php)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3730154A (en) * 1972-02-02 1973-05-01 Ford Motor Co Engine spark timing control
US3779220A (en) * 1972-03-08 1973-12-18 Ford Motor Co Distributor vacuum spark advance control valve with regulator
US3857373A (en) * 1972-12-01 1974-12-31 Chrysler 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
US3933166A (en) * 1974-05-10 1976-01-20 The Bendix Corporation Altitude compensated vacuum regulating valve
JPS5142336U (show.php) * 1974-09-04 1976-03-29
US4126084A (en) * 1973-10-11 1978-11-21 Masami Inada Ignition time adjuster for an internal combustion engine
JPS5420571A (en) * 1977-07-13 1979-02-16 Daimaru Shiki Kk Device of automatically cutting pasteboard
US4428343A (en) 1981-11-23 1984-01-31 General Motors Corporation Tip-in knock eliminating spark timing control
EP0257763A1 (en) * 1986-07-24 1988-03-02 Samuel Szloboda Vacuum operated apparatus for controlling the ignition timing of an engine
US5606947A (en) * 1995-03-29 1997-03-04 Hong; Fu C. Automotive acceleration-horsepower control means

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52140116U (show.php) * 1976-04-20 1977-10-24

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3730154A (en) * 1972-02-02 1973-05-01 Ford Motor Co Engine spark timing control
US3779220A (en) * 1972-03-08 1973-12-18 Ford Motor Co Distributor vacuum spark advance control valve with regulator
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
US3933166A (en) * 1974-05-10 1976-01-20 The Bendix Corporation Altitude compensated vacuum regulating valve
JPS5142336U (show.php) * 1974-09-04 1976-03-29
JPS5420571A (en) * 1977-07-13 1979-02-16 Daimaru Shiki Kk Device of automatically cutting pasteboard
US4428343A (en) 1981-11-23 1984-01-31 General Motors Corporation Tip-in knock eliminating spark timing control
EP0257763A1 (en) * 1986-07-24 1988-03-02 Samuel Szloboda Vacuum operated apparatus for controlling the ignition timing of an engine
US5606947A (en) * 1995-03-29 1997-03-04 Hong; Fu C. Automotive acceleration-horsepower control means

Also Published As

Publication number Publication date
DE2137234A1 (de) 1972-03-09
CA947158A (en) 1974-05-14
JPS5037817B1 (show.php) 1975-12-05
DE2137234B2 (de) 1979-08-30
DE2137234C3 (de) 1980-05-22
FR2103892A5 (show.php) 1972-04-14
GB1293713A (en) 1972-10-25

Similar Documents

Publication Publication Date Title
US3638626A (en) Engine spark timing control device
US3698366A (en) Engine spark timing control system
US3698371A (en) Surging prevention device for use in vehicle having multicylinder spark-ignition internal combustion engine
US3606871A (en) Engine spark timing control device
US3828743A (en) Altitude compensated vacuum amplifier
US3954091A (en) System for detoxicating exhaust gases
US3955364A (en) Engine deceleration vacuum differential valve control
US3765394A (en) Split engine operation
US3730154A (en) Engine spark timing control
US3805760A (en) Run-on prevention device for internal combustion engines
US3476094A (en) Internal combustion engine ignition spark vacuum advance mechanism delay system
US3678907A (en) Engine spark timing system
US3433242A (en) Fluid bypass and pressure relief valve assembly
US3712279A (en) Vacuum spark advance cutoff
US3857373A (en) Vacuum delay valve
US3081793A (en) Valve mechanism
US3353524A (en) Method of operating an automotive engine
US2918047A (en) Split engine
US4098850A (en) Orifice device for air flow restriction
US3486595A (en) Internal combustion engines
US3810452A (en) Engine spark timing system control
US3370577A (en) Vacuum control unit
US3788291A (en) Unitized distributor vacuum spark advance control valve with regulator
US3626914A (en) Ignition timing control and vacuum control unit
GB1230004A (show.php)