US3916862A - Torque rise limiting device - Google Patents

Torque rise limiting device Download PDF

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Publication number
US3916862A
US3916862A US409864A US40986473A US3916862A US 3916862 A US3916862 A US 3916862A US 409864 A US409864 A US 409864A US 40986473 A US40986473 A US 40986473A US 3916862 A US3916862 A US 3916862A
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United States
Prior art keywords
engine
fuel
limiting device
control member
bore
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Expired - Lifetime
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US409864A
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English (en)
Inventor
Jerry A Clouse
John H Parks
Millard D Potter
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.)
Caterpillar Inc
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Caterpillar Tractor Co
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Application filed by Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Priority to US409864A priority Critical patent/US3916862A/en
Priority to JP49121095A priority patent/JPS5073031A/ja
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Publication of US3916862A publication Critical patent/US3916862A/en
Assigned to CATERPILLAR INC., A CORP. OF DE. reassignment CATERPILLAR INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CATERPILLAR TRACTOR CO., A CORP. OF CALIF.
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Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/04—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered by mechanical means dependent on engine speed, e.g. using centrifugal governors

Definitions

  • governors are utilized to position a fuel pump feed rack of a compression ignition engine normally to maintain the engine speed within a predetermined operating range.
  • Such governors are shown in US Pat. Nos. 3,145,624 and 3,532,082 issued to Parks et al. and Clouse et al.; respectively, both of which are assigned to the assignee of the present application.
  • the load of the engine is increased the engine speed tends to decrease and the fuel rack is advanced to supply more fuel to the combustion chambers of the engine.
  • engine speed increases and the fuel pump feed rack is automatically retracted to reduce the supply of fuel to the engine.
  • a fixed, full load rack stop is normally provided to limit the maximum volume of fuel directed to the engine for establishing the full load speed of the engine.
  • the engine speed will decrease rapidly toward a lug condition.
  • the efficiency of the fuel pump increases as the engine speed decreases and a greater volume of fuel is delivered to the combustion chambers resulting in an inherent increase in the brake means effective pressure (BMEP) and the torque of the engine.
  • BMEP effective pressure
  • the natural torque rise under'such conditions is detrimental to effective control of noxious exhaust emissions from the engine.
  • the torque rise is too great, inefficient and incomplete buming of fuel results in excessive engine heat and an increase in the exhaust smoke.
  • an object of this invention is to provide an improved torque rise limiting device for an internal combustion engine.
  • Another object of this invention is to provide such a torque rise limiting device which limits the amount of torque rise experienced by the engine when its speed is decreased below a full load speed when a lug producing load is imposed on the engine.
  • Another object of this invention is to provide an improved torque rise limiting deviceof the character described which automatically decreases the volume of fuel directed to the engine when the engine speed decreases below a predetermined full load speedsetting due to a load imposed thereon to minimize the noxious exhaust emissions from the engine.
  • FIG. 4 is a longitudinal vertical sectional view of an alternate embodiment of the torque rise limiting device DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • a torque rise limiting device embodying the principle of the present invention is generally indicated by the reference numeral 10 in association with a speed responsive governor 11 of an internal combustion engine, not shown.
  • the governor is generallyof the type described in detail in the above cited patents to Parks et al. and Clouse et al. and is contained within a housing 12.
  • the housing includes a generally vertical wall 13 having a pair of spaced generally parallel bores 14 and 15 formed therethrough.
  • the governor includes a pair of substantially L- shaped flyweights l6 pivotally mounted on a rotatable carrier, not shown.
  • Each flyweight has a radially inwardly extending arm.l7 adapted to contact a thrust member 18 mounted on a cylindrical sleeve W.
  • sleeve extends within a bore 20 of a cylindrical collar 21 and is secured to the collar and a fuel control member or rack 22 with a pin 23.
  • The'collar includes an end wall 24 having a centrally disposed bore 25 extending axially therethrough.
  • a bifurcated throttle control lever 26 is pivotally mounted on a shaft 27 secured within the housing 12.
  • the throttle control lever is adapted for engagement with a spring retaining seat 28 which is disposed in concentric axially slidable relation on a support member 29.
  • the support member is fixedly secured to the housing wall 13 in substantially coaxial alignment with the bore 14 and includes a concentric axial bore 31 extending therethrough.
  • a governor spring 32 is concentrically disposed in a precompressed condition between the retainer seat and the collar.
  • the torque rise limiting device 10 of the present invention includes a hydraulic reaction or servo mechanism 34 reciprocably mounted within the bore 15in the wall 13 of the housing 12.
  • An annular groove 36 is formed in the bore, and is adapted to receive pressurized oil from an engine oil pump, not shown.
  • the servo mechanism includes a hollow cylinder 37 slidably disposed within the bore 15.
  • the cylinder has a coaxial bore 38 and includes a closed end 39 which is disposed adjacent to the control lever 26.
  • An exteriorly extending protuberance 40 is centrally formed on the closed end of the cylinder.
  • An orifice 41 extends radially through the wall of the cylinder adjacent the closed end thereof to communicate the bore of the cylinder with the groove.
  • a cap 42 is screw threadably secured to the open end of the cylinder and has a centrally disposed bore 43 and a plurality of angularly spaced apertures 44 extending therethrough.
  • a slotted tangportion 46 is provided on the end cap for slidably embracing an enlarged shank 47 of a guide member 48 which is screw threadably secured to the wall adjacent to the cylinder.
  • A-piston 49 is reciprocably mounted within the cylinder 37 and has a medially disposed annular wall 51 forming within the cylinder a pair of axially spaced chambers 52 and 53.
  • a centrally disposed aperture 54 extends axially through the annular wall to provide communication; .between the chambers.
  • a pair of springs 56 and 57 are individually disposed within the chambers on opposite sides of the piston and act in op- :posite directions normally to center the piston within the cylinder.
  • a bleed valve 58 is partially disposed within the chamber 52 and has a reduced diameter guide and actuation portion 59 slidably extending through the central bore 43 of the cap 42.
  • a recess 61 is provided in the end of the bleed valve adjacent to the annular wall and is formed in part by anannular axially extending .valve seat 62.
  • the valve seat is adapted for selective sealing engagement with the annular wall to block communication between the chambers 52 and 53 through-the aperture54.
  • a lever 63 is secured to the free end of a leaf type spring 64 which is in turn secured by a capscrew 65 to the wall 13 of the housing 12 to permit limited pivotal :movement of the lever.
  • the lever extends upwardly therefrom and includes a distal or free end 66 which'is adapted for abutment with the guide portion 59 of the bleed valve 58.
  • a pair of generally vertically spaced clearance holes 67 and 68 are provided in the lever intermediate itsends.
  • An elongated sensor and actuator member 69 is slidably disposed within the bore 31 of the support member 29.
  • An end 71 of the member extends through the bore 25 in the end wall 24 of the collar 21 and has an enlarged flange 72 formed thereon for unidirectional force transmitting engagement with the end wall.
  • An opposite end 73 of the actuator member extends through the bore 14 of wall 13 and the hole68 of the lever 63 and includes a circumferential groove 74 fomied therearound.
  • a bracket 76 includes a through bore 77 which is slidably received on the end 73 in radiably embraces a rod 87 secured to the housing 12 for preventing rotation of the bracket and the actuator member.
  • a cam 88 is secured between the bifurcated-portions of the control lever 26 for rotation therewith and has a cam lobe 89 formed thereon for engagementwith the protuberance 40 of the cylinder 37.
  • FIG. 3 Modified First Form A modification of the above embodiment is shown in FIG. 3 and includes an inwardly opening hole 90 which is formed in the closed end 39 of the cylinder 37 and is concentric with the bore 38.
  • An elongated stop pin 91 is pressed into the hole and has an enlarged head portion 92 in abutment with the annular wall 51 of the piston 49.
  • a recess 93 and a plurality of radially extending slots 94 are formed in the head portion adjacent to the annular wall for communicating the chamber 53 with the aperture 54 in the annular wall.
  • the length ofv the pin is selected to position the piston slightly to the left bf its position in FIG. 1 to unbalance the springs 56 and 57 with spring 56 having a greater preload than the spring 57.
  • the governor 11 functions to maintain the engine speed within a predetermined operating range by adjusting the position of the fuel control member 22 in the usual manner as the load on the engine varies.
  • the predetermined speed range is established by manual positioning of the throttle control lever 26 to provide a preload force on the governor spring 32 to act against the centrifugal force of the flyweights 16. Rotating the control lever in a counterclockwise direction results in movement of the fuel control member to the right to increase the volume of fuel injected into the engine to increase the engine speed.
  • the cylinder is moved to the left by the cam lobe 89 as the throttle control lever is rotated clockwise.
  • the change in the imbalance of the springs 56 and 57 balances the changing force of the governor spring such that the piston remains substantially stationary relative to the wall 1 3 Thl 1S the position of the fuel control member is virtually unaffected by the repositioning of the throttle controllever when the engine is operating at lugging speeds below the full load speed.
  • the torque rise limiting device is effective through thelentire range of throttle settings and engine speeds
  • the torque rise curve for an intermediate throttle control lever setting is shown at F in FIG. 7 with the curve joining the torque curve A at point G and continues to increase along the curve A to point D.
  • the torque curve of the engine without the present invention coincides with curve F with the torque continuing to increase past point G and joining the broken line curve E at point H.
  • the horsepower curve for the engine is represented by the line indicated by the letter J.
  • the governor spring 34 exerts a greater force on the bleed valve SS'which in turn causes the fluid pressure in the chamber 53 to increase.
  • the piston 49 will remain in abutment with the pin 91.
  • the fuel control member 22 will temporarily remain in the maximum fuel position and the engine torque will increase from point C in FIG. 7 along the broken line E.
  • the force exerted on the piston by the fluid and the spring 57 overcomes the:preload of the spring 56.
  • a pair of elongated slots 96 are provided in the collar individually to receive the ends of the pin 23 for permitting limited relative axial movement between the sleeve and the 'collar.
  • a keeper band 97 encircles the collar to prevent dislodgement of the pin.
  • the sleeve includes a reduceddiameter end portion 98 extending toward the end wall 24 of the collar.
  • Aconcentric axially extending bore 99 is provided in the reduced diameter portion and terminates at an end wall 101 having a central aperture 102 extending therethrough.
  • a ring 103 is disposed within the bore 20 of the collar with a spring 104 concentrically disposed between thejring and the sleeve and preloaded to a predetermined value for resiliently urging the sleeve and collar inopposite directions.
  • the torque rise limiting device of the alternate embodiment includes a mechanical reaction mechanism 106 which includes an adapter 107 disposed adjacent to the wall 13 of the housing 12.
  • the adapter has an annular extension 108 slidable within the bore of the wall.
  • An aperture 109 is provided in the adapter and slidably receives a shank 110 of a guide member 111 screw threadably secured to the wall to prevent rotation of the adapter.
  • a threaded bore 112 is provided through the annular extension for receiving an adjustable stop member 113 adapted for engagement with the cam lobe 89 of the control lever 26..
  • the adapter further includes a depending stop portion .114 for a later defined purpose. M v
  • a sensor tube 116 is reciprocably disposed in the bore 31 of the support member 29 and is provided with I an axial bore 117 which slidably receives an elongated actuator rod 1 18.
  • the actuator rod extends through the aperture 102 in the end wall 101 of the sleeve 19 and has an enlarged head portion 1 19 formed on its end for unidirectional force transmitting engagement with the end wall of the sleeve.
  • the bracket 76 secured to the end 73 of the sensor tube 116 has an inner surface 121 disposedadjacent to the wall 13 of the housing 12 and an opposite outersur- 1 face 122.
  • a recess 123 is formed in the inner surface to provide clearance for the stop portion 114 of the adapter 107 disposed between the bracket and the wall.
  • a pair of spaced lugs 124 are fixedly secured to the outer surface 122 and extend outwardly therefrom.
  • a bore 126 extends though the bracket in spacedsubstantially parallel relation to the bore77.
  • a pin 127 slidably extends through the bore 126 for engagement with the stop portion of the adapter and has a spherical head is formed on the side of the lever intermediate the pivot pin and slot and is adapted for engagement with the spherical head 128 of the pin 127.
  • An adjustment screw 137 is screw threadedly secured to the proximal end of the lever and has a jam nut 138 provided thereon for locking the adjustment screw in the ad- FIGS. 4, 5 and 6 operates the same asthat described above in connection with the first form in that when the load on the engine is increased the fuel control member 22 is normally adjusted to the right by the governor for supplying more fuel to the engine to maintain the engine speed within the desired operating range.
  • the torque rise limiting device and the governor are shown in thefull load speed condition in FIG. 4 with the fuel controlmember 22 in a position for supplying a predetermined maximum volume of fuel to the engine.
  • the fuel control member, the collar21, and the sleeve 19 arepositioned slightly to the left of that shown in FIG. 4 such that the head 119 of the actuator rod 118 is spaced somewhat from the end wall 101 of the sleeve and the enlarged flange 72 of the sensor tube 116 is spaced somewhat from the end wall 24 of the collar.
  • the governor 11 operates in the usual manner.
  • the engine With the control lever 26 in the position shown and the engine lightly loaded, the engine is set to operate at the high idle speed. Increasing the load on the engine results in the governor 11 moving the collar 21, sleeve 19, and fuel control member 22 to the right to increase the volume of fuel to the engine as previously described. At a predetermined speed, the end wall 24 of the collar engages the enlarged flange 72 of thesensor tube 116 and the end wall 101 of the sleeve 19 engages the head 1 19 of the actuator rod 1 18. This prevents further rightward movement of the fuel control member and establishes the full load speed condition of the engine. Y
  • the cam lobe 89 of the cam 88 moves the mechanical reaction mechai 9 nism 106 to the left at intermediate throttle settings. This moves the pin 127 to the left to establish the full load speed condition in accordance with the throttle control lever setting.
  • the torque rise curve of the engine equipped with the alternate embodiment torque rise limiting device is identical to that of the first form. However, by increasing the initial preload of the spring 104, the torque of the engine will increase along the broken line E in FIG. 7 until the force exerted by the governor spring 32 becomes sufficient to overcome the preload of the spring 104. At this point, which is represented by the letter K in FIG. 7, the torque rise limiting device becomes effective for controlling the torque rise with the torque being depicted by phantom line L.
  • the structure of the present invention provides an improved torque rise limiting device which limits the rate of torque rise of an internal combustion engine when the engine speed is decreased below its full load speed due to greater loading of the engine thereby reducing the volume of fuel injected into the engine.
  • This permits more efficient and complete combustion of the fuel to minimize the emission of noxious matter from the engine.
  • This is accomplished by automatic movement of the fuel control member to a reduced fuel setting in response to a conditional change of the governor created when the centrifugal force of the flyweights, balancing the force of the governor spring, is reduced to a decrease in engine speed.
  • the torque rise limiting device further automatically positions itself in response to a change in the throttle control lever setting so that the device effectively limits torque rise and minimizes exhaust emissions throughout the full range of throttle settings and engine operating speeds. While the invention has been described and shown.
  • a torque rise limiting device for an internal combustion engine having a speed responsive governor adapted normally to urge a fuel control member toward an increased fuel position when the load on the engine is increased, comprising;
  • reaction means operatively associated with said sensor and actuator means and responsive to a conditional change of the governor transmitted thereto by the sensor andactuator means when the speed of the engine decreases below a predetermined speed due to the load imposed thereon to impart a reaction force through the sensor and actuator .
  • a throttle control lever pivotal within the housing between a minimum and maximum engine speed setting
  • a governor spring operatively disposed between said control lever and the fuel control member for resiliently urging the fuel control member toward the increased fuel position
  • a flyweight arrangement responsive to engine speed normally to counterbalance the bias of the governor spring to minimize changes in engine speed due to varying engine loads with said conditional change of the governor causing an actuating force to be exerted on said reaction means by said governor spring through said sensor and actuator means.
  • reaction means includes;
  • ahydraulic servo mechanism reciprocably disposed in said bore and in communication with said source of pressurized fluid, said hydraulic servo mechanism having opposite ends with one of said ends adapted for engagement with the cam means while the other of said ends is adapted for engagement with said sensor and actuator means, said hydraulic servo mechanism being operative in response to said actuating force imposed thereon by said sensor and actuator means to generate a reaction force substantially equal to said actuating force with said reaction force being transmitted by the sensor and actuator means to move the fuel control membe toward said decreased fuel position.
  • an actuator member having opposite ends with one of said ends operatively connected to the fuel control member
  • a cylinder having an axial bore formed therein, siad bore having an open end and an opposite closed end, and an orifice communicating said bore with said source of pressurized fluid;
  • a cap secured tosaid open end of said cylinder having a plurality of apertures and a centrally disposed 1 1 bore extending therethrough'with said bore being substantially concentric with said bore of said cylinder;
  • a piston reciprocably mounted in said bore of said cylinder forming a first chamber between said piston and said closed end for receiving fluid from the source of pressurized fluid, and a second chamber between the piston and said cap, said piston having a centrally disposed aperture extending there- 1 through for communicating the first chamber with the second chamber;
  • positioning means for initially positioning said piston in said bore of the cylinder including a spring disposed in said second chamber;
  • a bleed valve slidably disposed in said bore of said cap and having opposite ends, a valve seat formed on one of said ends normally positioned to permit substantially unrestricted flow through said aperture in said piston and adapted for blocking fluid flow therethrough when said actuating force is exerted in a first direction on the other of said ends of said lever of said sensor and actuator means to generate said reaction force by increasing the fluid pressure in the first chamber to cause the piston to move in an opposite direction until the actuation force on the valve is balanced by the reaction force.
  • said positioning means includes stop means associated with said cylinder to limit movement of said piston toward said closed end of said cylinder.
  • said stop means includes a stop member disposed .within said first chamber between said closed end and said piston, said stop member having an end portion for engagement with said piston and passage means formed in said end portion for communicating said first chamber with said aperture in said piston.
  • the torque rise limiting device of claim 10 including a spring disposed in said first chamber between said piston and said closed end of said cylinder.
  • the torque rise limiting device of claim 3 includmg; 7 i
  • said sensor and actuator means includes an elongated sensor tube having opposite ends with one of said ends connected to said collar for selective unidirectional force transmitting engagement therewith, said tube having a bore extending axially therethrough;
  • an actuator rod slidably disposed in said bore of said sensor tube and having opposite ends with one of said ends having unidirectional driving connection with said sleeve for transmitting axial unidirectional movement thereto.
  • reaction means includes a mechanical reaction mechanism operatively attached to said sensor tube and to the other of said ends of actuator rod operative in response to said actuating force transmitting thereto by said sensor tube to generate a reaction force in the actuator rod for'moving the sleeve and the fuel control member toward the decreased fuel position against the bias of said spring disposed between said sleeve and said collar until the actuating force is balanced by the bias of said spring.
  • said mechanical reaction mechanism includes an adapter having an annular extension slidably disan end operatively connected to said other end of 7 said actuator rod, said lever having an intermediate portion engageable withthe other of said ends of said fulcrum pin so that movement of the sensor tube and bracket in a first direction causes the lever to pivot about the fulcrum pin to move the actuating rod in an opposite direction.
  • reaction means including a hydraulic servo mechanismcommunicating with said source of pressurized fluid having opposite ends with one of said ends operatively associated with such fuel control member, said hydraulic servo mechanism initially permitting the fuel control member to move toward an increased fuel position in response to a decrease in engine speed due to a load imposed thereon and being operative in response to a conditional change of the governor when the speed of the engine decreases below a predetermined speed due to the load imposed thereon to generate a reaction force to reverse the direction of movement of 13 the fuel control member and move the fuel control member toward a decreased fuel position so that the volume of fuel directed to the engine is reduced for limiting the natural torque rise thereof and minimrzmg the noxious exhaust emissions therefrom.
  • the torque rise limiting device of claim 17 including sensor and actuator means operatively associmember toward the decreased fuel position.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US409864A 1973-10-26 1973-10-26 Torque rise limiting device Expired - Lifetime US3916862A (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4026260A (en) * 1975-08-04 1977-05-31 Caterpillar Tractor Co. Speed sensitive fuel control system
US4082073A (en) * 1976-06-16 1978-04-04 General Motors Corporation Engine speed governor with improved peak load control
US4136658A (en) * 1977-01-17 1979-01-30 Caterpillar Tractor Co. Speed sensitive pressure regulator system
US4149507A (en) * 1977-10-27 1979-04-17 Caterpillar Tractor Co. Fuel-air ratio control with torque-limiting spring for supercharged engines
US4909216A (en) * 1986-12-12 1990-03-20 Mtu Friedrichshafen Gmbh Regulating arrangement of a fuel-injection pump with a lever
US5468126A (en) * 1993-12-23 1995-11-21 Caterpillar Inc. Hydraulic power control system
US5525043A (en) * 1993-12-23 1996-06-11 Caterpillar Inc. Hydraulic power control system
US5959420A (en) * 1997-12-01 1999-09-28 Chrysler Corporation Heat engine and electric motor torque distribution strategy for a hybrid electric vehicle
US20140130778A1 (en) * 2014-01-21 2014-05-15 Caterpillar Inc. Method of operating engine

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2868184A (en) * 1957-04-22 1959-01-13 Curtiss Wright Corp Engine load limiting controls
US3107483A (en) * 1961-06-08 1963-10-22 Allis Chalmers Mfg Co Fuel control for engines
US3145702A (en) * 1962-04-25 1964-08-25 Caterpillar Tractor Co Engine speed limiter controlled by lubricating oil pressure
US3234927A (en) * 1963-06-24 1966-02-15 Murphy Diesel Company Torque control device for diesel engines
US3358664A (en) * 1965-06-21 1967-12-19 Holley Carburetor Co Engine control device
US3613651A (en) * 1969-09-15 1971-10-19 Ambac Ind Minimum-maximum governor with full load torque control
US3640258A (en) * 1969-08-04 1972-02-08 Diesel Kiki Co Governor for internal combustion engines of injection type
US3707144A (en) * 1971-07-01 1972-12-26 Ambac Ind Fuel control device for fuel injection pump governors
US3777730A (en) * 1972-03-20 1973-12-11 Caterpillar Tractor Co Fuel limiting device
US3795233A (en) * 1972-05-19 1974-03-05 Caterpillar Tractor Co Fuel-air ratio control for supercharged engines
US3797470A (en) * 1972-02-10 1974-03-19 Teledyne Ind Fuel regulating system for an internal combustion engine
US3814072A (en) * 1972-06-06 1974-06-04 Woodward Governor Co Manifold pressure controller fuel limiter

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2868184A (en) * 1957-04-22 1959-01-13 Curtiss Wright Corp Engine load limiting controls
US3107483A (en) * 1961-06-08 1963-10-22 Allis Chalmers Mfg Co Fuel control for engines
US3145702A (en) * 1962-04-25 1964-08-25 Caterpillar Tractor Co Engine speed limiter controlled by lubricating oil pressure
US3234927A (en) * 1963-06-24 1966-02-15 Murphy Diesel Company Torque control device for diesel engines
US3358664A (en) * 1965-06-21 1967-12-19 Holley Carburetor Co Engine control device
US3640258A (en) * 1969-08-04 1972-02-08 Diesel Kiki Co Governor for internal combustion engines of injection type
US3613651A (en) * 1969-09-15 1971-10-19 Ambac Ind Minimum-maximum governor with full load torque control
US3707144A (en) * 1971-07-01 1972-12-26 Ambac Ind Fuel control device for fuel injection pump governors
US3797470A (en) * 1972-02-10 1974-03-19 Teledyne Ind Fuel regulating system for an internal combustion engine
US3777730A (en) * 1972-03-20 1973-12-11 Caterpillar Tractor Co Fuel limiting device
US3795233A (en) * 1972-05-19 1974-03-05 Caterpillar Tractor Co Fuel-air ratio control for supercharged engines
US3814072A (en) * 1972-06-06 1974-06-04 Woodward Governor Co Manifold pressure controller fuel limiter

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4026260A (en) * 1975-08-04 1977-05-31 Caterpillar Tractor Co. Speed sensitive fuel control system
US4082073A (en) * 1976-06-16 1978-04-04 General Motors Corporation Engine speed governor with improved peak load control
US4136658A (en) * 1977-01-17 1979-01-30 Caterpillar Tractor Co. Speed sensitive pressure regulator system
US4149507A (en) * 1977-10-27 1979-04-17 Caterpillar Tractor Co. Fuel-air ratio control with torque-limiting spring for supercharged engines
US4909216A (en) * 1986-12-12 1990-03-20 Mtu Friedrichshafen Gmbh Regulating arrangement of a fuel-injection pump with a lever
US5468126A (en) * 1993-12-23 1995-11-21 Caterpillar Inc. Hydraulic power control system
US5525043A (en) * 1993-12-23 1996-06-11 Caterpillar Inc. Hydraulic power control system
US5959420A (en) * 1997-12-01 1999-09-28 Chrysler Corporation Heat engine and electric motor torque distribution strategy for a hybrid electric vehicle
US20140130778A1 (en) * 2014-01-21 2014-05-15 Caterpillar Inc. Method of operating engine

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Publication number Publication date
JPS5073031A (de) 1975-06-17

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AS Assignment

Owner name: CATERPILLAR INC., 100 N.E. ADAMS STREET, PEORIA, I

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515

Owner name: CATERPILLAR INC., A CORP. OF DE.,ILLINOIS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515