US3885536A - Recirculating exhaust gas load initiated control (relic) - Google Patents

Recirculating exhaust gas load initiated control (relic) Download PDF

Info

Publication number
US3885536A
US3885536A US408953A US40895373A US3885536A US 3885536 A US3885536 A US 3885536A US 408953 A US408953 A US 408953A US 40895373 A US40895373 A US 40895373A US 3885536 A US3885536 A US 3885536A
Authority
US
United States
Prior art keywords
vacuum
egr
valve
air
manifold
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
US408953A
Other languages
English (en)
Inventor
John R Marshall
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
Priority to US408953A priority Critical patent/US3885536A/en
Priority to AU73703/74A priority patent/AU477953B2/en
Priority to GB4201074A priority patent/GB1451853A/en
Priority to CA211,380A priority patent/CA1021651A/en
Priority to DE19742449431 priority patent/DE2449431A1/de
Priority to JP12043374A priority patent/JPS531418B2/ja
Application granted granted Critical
Publication of US3885536A publication Critical patent/US3885536A/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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/55—Systems for actuating EGR valves using vacuum actuators
    • F02M26/56—Systems for actuating EGR valves using vacuum actuators having pressure modulation valves

Definitions

  • the engine has a duct connecting the gases in the exhaust gas crossover passage to the intake manifold, the duct normally being closed by a valve that is opened by manifold vacuum modulated as a function of carburetor throttle blade opening (EGR port vacuum) and connected to the valve by a vacuum regulator having an air-bleed that is controlled by manifold vacuum so that the gas recirculating valve opening signal force varies with load during part throttle operations and idle to prevent recirculation during engine idle and cruising and wide-open throttle operations while providing controlled operation in the engine accelerating range between.
  • EGR port vacuum carburetor throttle blade opening
  • This invention relates, in general, to an internal combustion engine. More particularly, it relates to a system for controlling the recirculation of exhaust gases back into the engine through the intake manifold.
  • Devices for recirculating a portion of the engine exhaust gases back through the engine to control the emission of unburned hydrocarbons and lower the output of oxides of nitrogen. These devices have included valving to prevent recirculation of the exhaust gases at undesired times and generally are controlled by movement of the carburetor throttle valve so that recirculation is prevented during engine idle and wideopen throttle operations. This is desirable because at engine idle, exhaust gas scavenging is inefficient, while at wide-open throttle position, maximum power is limited by the availability of oxygen.
  • EGR exhaust gas recirculation
  • FIG. 1 is a cross-sectional view of a portion of an internal combustion engine and associated carburetor embodying the invention
  • FIG. 2 is a cross-sectional view taken on a plane indicated by and viewed in the direction of the arrows 2-2 of FIG. I;
  • FIG. 3 is a modification.
  • FIG. 1 illustrates a portion of one-half of a twobarrel carburetor of a known downdraft type. It has an air horn section 12, a main body portion 14, and a throttle body 16, joined by suitable means not shown.
  • the carburetor has the usual air/fuel induction passages 18 open at their upper ends 20 to fresh air from the conventional air cleaner, not shown.
  • the passages 18 have the usual fixed area venturies 22 cooperating with booster venturies 24 through which the main supply of fuel is induced, by means not shown.
  • Flow of air and fuel through induction passages 18 is controlled by a pair of throttle valve plates 26 each fixed on a shaft 28 rotatably mounted in the side walls of the carburetor body.
  • the throttle body 16 is flanged as indicated for bolting to the top of the engine intake manifold 30, with a spacer element 32 located between.
  • Manifold has a number of vertical risers or bores 34 that are aligned for cooperation with the discharge end of the carburetor induction passages 18.
  • the risers 34 extend at right angles at their lower ends 36 for passage of the mixture out of the plane of the figure to the intake valves of the engine.
  • the exhaust manifolding part of the engine cylinder head is indicated partially at 38, and includes an exhaust gas crossover passage 40.
  • the latter passes from the exhaust manifold, not shown, on one side of the engine to the opposite side beneath the manifold trunks 36 to provide the usual hot spot" beneath the carburetor to better vaporize the air/fuel mixture.
  • the spacer 32 is provided with a worm-like recess 42 that is: connected directly to cross-over passage 40 by a bore 44. Also connected to passage 42 is a passage 46 alternately blocked or connected to a central bore or passage 48 communicating with the risers 34 through a pair of ports 50. Mounted to one side of the spacer is a cup shaped boss 52 forming a chamber 54 through which passages 46 and 48 are interconnected.
  • passage 46 normally is closed by a valve 56 that is moved to an open position by a servo 58.
  • the servo includes a hollow outer shell 64 containing an annular flexible diaphragm 66. The latter divides the interior into an air chamber 68 and a signal vacuum chamber 70. Chamber 68 is connected to atmospheric pressure through a vent 72, while chamber 70 is connected to a vacuum signal force through a line 74.
  • the stem of valve 56 is fixed to a pair of retainers 76 secured to diaphragm 66. They serve as a seat for a compression spring 77 normally biasing the valve to its closed position.
  • the stem slidably and sealingly projects through a plate 78 closing chamber 54.
  • the carburetor contains a manifold vacuum sensing port 80 and an exhaust gas recirculating (EGR) port 82.
  • EGR exhaust gas recirculating
  • the latter is located above the port 80 and above the closed position of throttle valve 26 to be traversed by the edge of the throttle valve as it moves open.
  • the pressure in. port 82 thereby varies from atmospheric to the manifold vacuum level as a function of the opening of throttle valve 28.
  • Port 82 is connected through a vacuum regulating device 84 in passage 74 to servo 58.
  • Device 84 in this case is manifold vacuum controlled to regulate the flow of EGR vacuum to servo 58 in proportion to engine load. More specifically, device 84 includes a vacuum switch 86 in a series with an EGR signal vacuum regulator 88 to bleed EGR vacuum as a function of throttle valve position when the manifold vacuum is above a certain level. As shown schematically in FIG. 1, both the vacuum switch 86 and vacuum regulator 88 are constructed alike. They consist of outer housings 90, 90 divided into two chambers 92, 92 and 94, 94' by annular flexible diaphragms 96, 96. The lower shell portions are formed with two passages 98, 98 and 100, 100.
  • the vacuum switch 86 controls the bleed of air to the vacuum regulator 88 as a function of manifold vacuum level.
  • Chamber 92 is connected by a passage 110 to manifold vacuum port 80.
  • Lower passage 98 is vented to atmosphere, while passage 100 is connected by a passage 112 to lower passage 98 of the vacuum regulator 88. If the force of spring 104 is chosen, for example, to be such as to keep diaphragm 96 against seat 102 until the manifold vacuum rises above 7 inches Hg., then the diaphragm will block off the bleed of air into passage 100 for all vacuum levels below 7 inches Hg.
  • the vacuum regulator 88 regulates the EGR signal vacuum to the EGR valve 56 by at times bleeding it, with the air from the vacuum switch 86.
  • the EGR vacuum in port 82 is connected by a line 114 through parallel lines 116 and 118 to the upper chamber 92' and lower passage 100 respectively, of the regulator valve, as well as to the line 74 leading to the EGR valve.
  • the spring 104 in this case would be chosen to have a force such that would maintain the diaphragm 96' seated to block passage 100 below say 3 inches Hg., EGR vacuum force, for example.
  • the throttle valve 26 is moved to a slightly open position for light accelerations of the vehicle.
  • the manifold vacuum most likely will not decay below a vacuum level of 7 inches Hg., therefore, the vacuum switch 86 will remain open, bleeding air in passage 98 into the open end of passage 100 to the air passage 98 of the vacuum regulator 88.
  • the EGR vacuum in port 82 will be modulating the manifold vacuum as the throttle valve traverses the EGR port. Assume, therefore, that the EGR vacuum at this time is above 3 inches Hg. This then causes the diaphragm 96' to move off the conical seat 102 and permit bleed of the EGR vacuum level in passage 100 by the air in passages 98'.
  • This bleed will decay the EGR vacuum signal force to the EGR valve 56 until an equilibrium position is obtained in which the forces of the EGR vacuum plus the spring force acting on the upper side of diaphragm 96 are sufficient to seat it against the conical seat 102.
  • the EGR vacuum will then regulate at the lower vacuum force level, thus providing a small amount of EGR flow and one corresponding essentially to the light load operation.
  • FIG. 1 illustrates the vacuum switch 86 and vacuum regulator 88 somewhat schematically
  • FIG. 3 shows a preferred integrated and more to scale construction.
  • the combined vacuum switch and vacuum amplifier are housed within a three piece outer housing 120 having a central partition 122 dividing the housing into two main sections 124 and 126.
  • a first annular flexible diaphragm 128 subdivides the chamber 126 into a pair of chambers 130 and 132.
  • Chamber 130 is connected to manifold vacuum through a passage 134 connected to intake manifold port 80.
  • Chamber 132 is connected or vented to air at atmospheric pressure through a passage 136.
  • the vacuum regulator portion 124 of the housing likewise is further subdivided by an annular flexible diaphragm 138 into two chambers 140 and 142.
  • the chamber 140 is connected by a passage 144 to the EGR vacuum port 82 as well as to the EGR valve line 74.
  • Chamber 142 is connected to the vent passage 136 by a pair of intersecting passages 146 and 148 through the center partition 122.
  • a compression spring 150 is seated between the diaphragm 128 and an adjustable stop 152 slidable in the shell 120.
  • a compression spring 154 is seated between the diaphragm 138 and a second adjustable stop 156 slidable in the housing 120.
  • the force of spring 150 would be chosen so as to be comparable to the force of spring 104 of the vacuum switch, and, in that respect, would be approximately equal to 7 inches Hg.
  • the force of spring 154 likewise would be similar to that of the force of spring 104' of the vacuum regulator, and would be approximately equal to 3 inches Hg.
  • the spring 150 biases the diaphragm 128 against the open end of the passage 148 in partition 122; thus, when seated, blocking the bleed of air into the annular chamber 142.
  • the spring 154 biases the diaphragm 138 against the opposite side of the partition 122, which in this case is closed off.
  • a through port 158 in provided through the diaphragm retainer.
  • the invention provides an EGR flow rate during part throttle operations that is nearly proportional to engine load so that during maximum accelerations a maximum flow capacity is obtained, whereas during light load operation, only little flow is provided. Likewise, it will be seen that the invention prevents large flow when wide open throttle conditions of operation occur because at that time the EGR port vacuum is nearly zero.
  • An exhaust gas recirculating system in an internal combustion engine having intake and exhaust manifolds and a carburetor induction passage having a throttle valve controlling flow through the passage comprising, a duct connecting the exhaust gases to the engine intake manifold, an exhaust gas recirculation (EGR) valve normally closing the duct to prevent recirculation and movable to an open position by a signal vacuum connected thereto, and modified manifold vacuum responsive means operable to provide a signal vacuum to the valve that varies from one pressure level at closed or nearly closed throttle positions to manifold vacuum levels near wide open throttle positions in response to movement of the throttle valve and changes in manifold vacuum to provide an EGR flow rate that varies essentially in proportion to the load during part load operation, the induction passage containing an EGR port located relative to the throttle valve so as to be traversed by the edge of the throttle valve upon opening movements of the throttle valve so as to be at essentially atmospheric pressure at closed throttle positions with decreases in pressure level in proportion to the progressive opening of the throttle valve until EGR port vacuum
  • the regulator including an atmospheric air passage, a flexible diaphragm type vacuum valve having spring means biasing the diaphragm against the air passage closing the same, means applying EGR vacuum to the diaphragm to move the vacuum valve to open the air passage and bleed down the EGR vacuum,
  • the switch means including a second flexible diaphragm valve, other means supplying air to the air passage, second spring means biasing the second diaphragm valve to a position blocking the other means, the second diaphragm valve being responsive to manifold vacuum above the force of the second spring means to move the second diaphragm valve to open the other means and permit airflow to the air passage for control by EGR vacuum to regulate EGR signal vacuum.
  • the regulator including an air passage having an inlet and outlet, 21 first valve that is spring movable to a first position against the air outlet blocking the same and blocking EGR signal vacuum flow from one side of the valve to the other, the first valve being responsive to EGR signal vacuum applied to the one side of the first valve to move the first valve to a second position unblocking the air outlet and permitting flow of air to the one side to decay the EGR signal vacuum, a second valve spring movable against the air inlet to block the same and movable by a predetermined level of manifold vacuum applied thereto to a second position opening the inlet to permit flow of air to the outlet, whereby EGR signal vacuum level to the EGR valve is regulated as a function of manifold vacuum above the predetermined level effecting the decay of EGR port vacuum to vary essentially proportional to load at part throttle operations.
  • the vacuum regulator including a first flexible diaphragm exposed to a chamber pressure on one side and EGR port vacuum on the other side, a second flexible diaphragm exposed to manifold vacuum on one side and to a source of air on the other side, the diaphragms both being spring seated to block the flow of air to the chamber past the first and second diaphragms to bleed the EGR port vacuum, movement of the second diaphragm to an unseated position by manifold vacuum above a predetermined level portion to load during accelerations, the unseating of and the first diaphragm by EGR port vacuum above a the first diaphragm by EGR port vacuum to the EGR predetermined level regulating the EGR port vacuum valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
US408953A 1973-10-23 1973-10-23 Recirculating exhaust gas load initiated control (relic) Expired - Lifetime US3885536A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US408953A US3885536A (en) 1973-10-23 1973-10-23 Recirculating exhaust gas load initiated control (relic)
AU73703/74A AU477953B2 (en) 1974-09-25 Recirculating exhaust gas load initiated control
GB4201074A GB1451853A (en) 1973-10-23 1974-09-27 Exhaust gas recirculating system
CA211,380A CA1021651A (en) 1973-10-23 1974-10-15 Recirculating exhaust gas load initiated control (relic)
DE19742449431 DE2449431A1 (de) 1973-10-23 1974-10-17 Abgasrueckfuehreinrichtung bei verbrennungsmotoren
JP12043374A JPS531418B2 (enrdf_load_stackoverflow) 1973-10-23 1974-10-21

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US408953A US3885536A (en) 1973-10-23 1973-10-23 Recirculating exhaust gas load initiated control (relic)

Publications (1)

Publication Number Publication Date
US3885536A true US3885536A (en) 1975-05-27

Family

ID=23618435

Family Applications (1)

Application Number Title Priority Date Filing Date
US408953A Expired - Lifetime US3885536A (en) 1973-10-23 1973-10-23 Recirculating exhaust gas load initiated control (relic)

Country Status (5)

Country Link
US (1) US3885536A (enrdf_load_stackoverflow)
JP (1) JPS531418B2 (enrdf_load_stackoverflow)
CA (1) CA1021651A (enrdf_load_stackoverflow)
DE (1) DE2449431A1 (enrdf_load_stackoverflow)
GB (1) GB1451853A (enrdf_load_stackoverflow)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4031871A (en) * 1976-03-02 1977-06-28 Toyota Jidosha Kogyo Kabushiki Kaisha Exhaust gas recirculation system of a motor vehicle
US4057043A (en) * 1975-06-13 1977-11-08 Nissan Motor Co., Ltd. Exhaust gas recirculation system
US4071006A (en) * 1975-08-12 1978-01-31 Nissan Motor Co., Ltd. Exhaust gas recirculating system
US4111172A (en) * 1974-11-30 1978-09-05 Nissan Motor Company, Limited System to feed exhaust gas into the induction passage of an internal combustion engine
US4114576A (en) * 1976-06-09 1978-09-19 Toyota Jidosha Kogyo Kabushiki Kaisha Exhaust gas recirculating control system

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5263512A (en) 1975-11-19 1977-05-26 Nissan Motor Co Ltd Control device against operation negative pressure
FR2378946A1 (fr) * 1977-01-28 1978-08-25 Renault Dispositif de recirculation de gaz d'echappement de moteurs a combustion interne
JPS53120019A (en) * 1977-03-30 1978-10-20 Hitachi Ltd Control valve for exhaust gas reflux device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3542004A (en) * 1968-08-09 1970-11-24 George W Cornelius Recycle apparatus
US3796049A (en) * 1971-12-25 1974-03-12 Nissan Motor Exhaust gas recirculation system for an internal combustion engine
US3812832A (en) * 1973-01-08 1974-05-28 Eaton Corp Dual function thermal valve
US3818880A (en) * 1972-08-02 1974-06-25 Chrysler Corp Exhaust gas recirculation control for internal combustion engines

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3542004A (en) * 1968-08-09 1970-11-24 George W Cornelius Recycle apparatus
US3796049A (en) * 1971-12-25 1974-03-12 Nissan Motor Exhaust gas recirculation system for an internal combustion engine
US3818880A (en) * 1972-08-02 1974-06-25 Chrysler Corp Exhaust gas recirculation control for internal combustion engines
US3812832A (en) * 1973-01-08 1974-05-28 Eaton Corp Dual function thermal valve

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4111172A (en) * 1974-11-30 1978-09-05 Nissan Motor Company, Limited System to feed exhaust gas into the induction passage of an internal combustion engine
US4057043A (en) * 1975-06-13 1977-11-08 Nissan Motor Co., Ltd. Exhaust gas recirculation system
US4071006A (en) * 1975-08-12 1978-01-31 Nissan Motor Co., Ltd. Exhaust gas recirculating system
US4031871A (en) * 1976-03-02 1977-06-28 Toyota Jidosha Kogyo Kabushiki Kaisha Exhaust gas recirculation system of a motor vehicle
US4114576A (en) * 1976-06-09 1978-09-19 Toyota Jidosha Kogyo Kabushiki Kaisha Exhaust gas recirculating control system

Also Published As

Publication number Publication date
CA1021651A (en) 1977-11-29
JPS5073030A (enrdf_load_stackoverflow) 1975-06-17
DE2449431A1 (de) 1975-04-24
GB1451853A (en) 1976-10-06
JPS531418B2 (enrdf_load_stackoverflow) 1978-01-19
AU7370374A (en) 1976-04-01

Similar Documents

Publication Publication Date Title
US3774583A (en) Venturi vacuum responsive exhaust gas recirculation control system
US3884200A (en) Exhaust gas recirculation control system for internal combustion engines
US3954091A (en) System for detoxicating exhaust gases
US3992878A (en) Engine secondary air flow control system
GB1486651A (en) Internal combustion engine having an exhaust gas recirculation system with an exhaust gas flow control valve
US3768452A (en) Engine exhaust gas recirculating control
US3885538A (en) Engine air pump pressure/manifold vacuum controlled exhaust gas recirculating control system
US4033309A (en) Exhaust gas recirculation system with control apparatus for exhaust gas flow control valve
US3842814A (en) Exhaust gas recirculation system
US3930475A (en) Engine exhaust gas recirculating control
US3928966A (en) Flow control valve for exhaust gas recirculation system
US3885536A (en) Recirculating exhaust gas load initiated control (relic)
US3970061A (en) Control system for exhaust gas recirculating valve
US3977381A (en) Exhaust gas recirculation system
US3460814A (en) Fuel-air mixture intake systems for internal combustion engines
US4398525A (en) Multi-stage exhaust gas recirculation system
US3835827A (en) Exhaust and gas recirculating system
US3885537A (en) Road load modulated exhaust gas recirculation system
US3878823A (en) Carburetor venturi vacuum and engine manifold vacuum controlled exhaust gas recirculating
US4098850A (en) Orifice device for air flow restriction
US3712279A (en) Vacuum spark advance cutoff
US3748855A (en) Reactor air flow control valve
US4398524A (en) Exhaust gas recirculation system
US4048967A (en) System for detoxicating exhaust gases
US4144856A (en) Exhaust gas recirculation system