US3640258A - Governor for internal combustion engines of injection type - Google Patents

Governor for internal combustion engines of injection type Download PDF

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Publication number
US3640258A
US3640258A US60221A US3640258DA US3640258A US 3640258 A US3640258 A US 3640258A US 60221 A US60221 A US 60221A US 3640258D A US3640258D A US 3640258DA US 3640258 A US3640258 A US 3640258A
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US
United States
Prior art keywords
oil
spring
governor
pressure
force
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
US60221A
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English (en)
Inventor
Hiroshi Isobe
Hachiro Aoki
Noritoshi Tanaka
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.)
Bosch Corp
Original Assignee
Diesel Kiki Co Ltd
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 Diesel Kiki Co Ltd filed Critical Diesel Kiki Co Ltd
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Publication of US3640258A publication Critical patent/US3640258A/en
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    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D13/00—Control of linear speed; Control of angular speed; Control of acceleration or deceleration, e.g. of a prime mover
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
    • F02D2700/02—Controlling by changing the air or fuel supply
    • F02D2700/0269—Controlling by changing the air or fuel supply for air compressing engines with compression ignition
    • F02D2700/0282—Control of fuel supply
    • F02D2700/0284—Control of fuel supply by acting on the fuel pump control element
    • F02D2700/0292—Control of fuel supply by acting on the fuel pump control element depending on the speed of a centrifugal governor

Definitions

  • the object of this invention is to provide a novel governor capable of the excellent control performance likethat of the fluid governor and yet constructed as simple as the centrifugal governor.
  • FIG. 1 shows in a cross section a governor constructed according to the invention
  • FIG. 2 shows in a perspective view a guide lever portion of said governor
  • FIG. 3 is a graph showing a discharge performance curve of a hydraulic pump employed in said governor
  • FIG. 4 is a discharge pressure graph for said pump
  • FIG. 5 is a graph showing the characteristic curves representing effects of control action of a control valve employed in said governor
  • FIG. 6 is a graph showing governor performance curves
  • FIG. 7 is a graph showing the characteristics of output torque for a diesel engine equipped with the governor of the invention.
  • FIG. 8 is a graph comparing the speed characteristics of output torque for a conventional diesel engine and a conventional gasoline engine.
  • a flyweight holder 3 rigidly mounted on a camshaft 2 of a fuel-injection pump 1, carries flyweights 5, which are pivotally mounted thereon by means of pivot pins 4.
  • the cylinder 3a forming an extension of the flyweight holder 3 on the side opposite to the camshaft 2 is connected by oldham coupling 6 to the drive shaft 8 of a hydraulic pump 7 such as a trochoid pump.
  • the pump 7 is built in the lower part of a governor case and serves as source of hydraulic pressure.
  • the drive shaft 8 extends out in the direction opposite to Oldham coupling 6 through the governor case 15; its end portion, outside the case 15, is threadedly fitted with a bolt 39 having a square recess in its head.
  • the bolt 39 holds a circular plate 38 fitted onto the drive shaft 8 this plate 38 is located to the drive shaft 8 by means of its slot 38a, into which is engaged a pawl 8a formed of the end portion of the shaftA lock washer 40, whose tongues are engaged with the slot 38a on the one hand and bear against the bolt 39 on the other, is fastened down by the bolt 39, so that this bolt is made unable to turn relative to the drive shaft 8.
  • circular plate 38 is retained on the shaft 8 in such a position as will provide a small running clearance between its inside face and the outer surface of the governor case 15.
  • the trochoid pump 7 lifts oil within the governor, and delivers pressurized oil from a discharge opening 9, provided in the lower part of the governor case 15, to an oil-pressure nor case 15 into which it is force fitted.
  • a movable cylinder 11 is urged toward the right, as viewed in FIG. 1, by a power-;-
  • a fuel adjusting rod 14 which form a part of fuel injection pump 1 and is positioned parallel to the movable cylinder 11, is connected with flange 1 1a.
  • the distal end of a stopper lever 18a, integral with a stop lever 18, can bear against the face of the flange 11a opposite to the other fac supporting a power spring 16.
  • the stop lever 18 is rotatably'i mounted on a stopper lever shaft 17 held rigidly by the governor case 15, and is so adapted that, by an operating handle 20 at the control station to turn the stop lever 18 in the direction of the arrow, the fuel-adjusting rod 14 can be pulled in the direction decreasing fuel-injection quantity.
  • the limit of the angular travel of the stop lever 18 returning (in the direction opposite to the arrow) is determined by the position of an adjustable stopper 19 secured to the governor case, to limit the maximum fuel-injection quantity.
  • the closed end of the cylinder 11 comes into contact with a pushrod 22 extending from a bush 23 and backed by a damper spring 21 contained in said bush 23, when the fuel-adjusting rod (14) is pulled back all the way in the direction decreasing fuel-injection quantity.
  • the bush 23 can be screwed in or out to repose it axially for adjustment by turning it with a screwdriver put to the slot cut in its outer end face, where a locknut 24, run from outside onto the portion of the bush 23 protruding from the boss part 15a, secures the bush 23 in its set position.
  • the oil-pressure supply opening 10 communicates to ports 25a and 25b provided in sleeve 25, which is force fitted into and rigidly held in a hole drilled out in the boss part 15b of the governor case. This communication is through the oil hole 10a and its extension.
  • Oil pressure applying through said oil hole 10a, acts upon the face 26c of the control valve 26 through said port 25b.
  • the other end face of the valve 26 is acted on by a control spring 27, which urges the valve 26 toward the right, in FIG. 1, by seating on the closed end of a spring holder 28.
  • This holder 28, slidably fitted onto and surrounding the protruding portion of the sleeve 25, is capable of axial movement.
  • valve 26 During operation, as the valve 26 is made to slide to and fro in the bore of the sleeve 25, its piston portion 26a covers and uncovers a port 25a, thereby controlling the extent of opening A at this port.
  • the sleeve 25 is provided with an another port 250, located diametrally opposite to said port 25a.
  • the outer end face of a holder 28, which is urged by a spring 27 toward the left side bears against a cam 31.
  • This cam is integral with a governor lever 30, which is interconnected by linkage to the accelerator pedal at the control station.
  • the lift of the cam 31 changes with the angular position of the governor lever 30 pivoting on a shaft 29 held rigidly by the governor case.
  • the open end of the holder 28 is formed with a flange 28a.
  • a torsion spring 35 is provided around the guide lever shaft 33 in such a way as to present a force opposing to the thrust sleeve 32 exerted when the centrifugal force of the flyweights 5 acts on this sleeve.
  • the torsional preload or set load given to the spring 35 can be varied for adjustment by turning a adjusting bolt 37, held by the governor case: turning the bolt 37 changes the angular position of a stopper 36 secured to the distal portion of the shaft 33 to rotate this shaft.
  • torsional spring 35 contemplated in the present embodiment may be supplanted by an ordinary coil spring.
  • the pressure P varies as the area of opening through which the oil is discharged, that is, opening "A" at the port 2511 is varied.
  • a rise in pressure P breaks the balance existing between oil pressure of the chamber 13 and power spring 16 and causes this cylinder 11, to slide toward the left, FIG. 1, to pull the fuel-adjusting rod 14 in the direction decreasing fuel-injection quantity until a new balanced state is reached.
  • the engine speed starts falling and decreases until the engine output balances with the reduced engine load. After the balance is reestablished between load and output, the engine runs in a steady-state condition. For an increase in engine load, on the other hand, the foregoing sequence of events takes place but in reverse order.
  • the object of the mechanism including the control valve 26, the spring 27, the sleeve 25 and the spring holder 28 is to provide a wider speed regulation for the control range covering idling speed and intermediate speeds of the engine in order to make the output characteristic approximate to that of the gasoline engine, so that the engine will not hunt during idling condition and, during intermediate-speed operation, the driver will get the same feel" as he would get when driving a vehicle with a gasoline engine.
  • This connection is illustrated in FIG. 5, wherein the speed N" is taken on the coordinate and the adjusting rod position R on the abscissa, with the area of opening A at the port 25a taken as a parameter.
  • the governor lever angle is taken also as a parameter.
  • This position of the stopper 18a can be varied by means of the stopper bolt 19.
  • the Bosch-type fuel injection pump whose beginning of injection occurs at the moment the head of a rising plunger has just covered the inlet port provided in the barrel, it is necessary to match the camshaft 2 to the engine crankshaft in phase relationship, so that the beginning of injection" of the pump will be in step with the prescribed beginning of injection in the engine.
  • This matching can be effected by referring to the timing marks provided on the plate 38 and on the governor case 15.
  • its drive shaft may be coupled to the drive shaft 8 by inserting the end of the former into a square recess 39 provided in the outer end of the shaft 8.
  • the governor according to the invention compensates the hydraulic pressure by means of the control valve for a change in speed, so that an adequate controlling force is secured for the engine in low-speed running condition.
  • the invention provides an all-speed governor in which lever reaction force is small.
  • FIG. 7 wherein the output torque T is taken on the coordinate and the engine speed N" on the abscissa, with the accelerator pedal positions (11,, (b (d taken as a parameter, refers to a diesel engine equipped with a governor according to the invention.
  • the governor according to this invention provides as high a rate of acceleration for a given stroke of the accelerator pedal as that of gasoline-engine vehicles, thereby improving the feel of acceleration the driver senses in accelerating the engine, and, for changes in load of the kind mentioned above, makes it unnecessary for the driver to possess a high degree of driving skill.
  • the above novel features are made possible in a relatively simple governor construction to add to the practical value of the governor according to the invention.
  • a governor for an internal combustion engine of the injection type comprising: an oil supply means for supplying oil under a pressure which varies with the rotational speed of the engine; a pressure actuated cylinder means for reciprocating a fuel-adjusting rod of the injection pump in response to pressure of oil supplied by said oil supply means; a first spring means operating on said cylinder means in opposition to the force exerted on the cylinder means by the pressure of said oil from the oil supply means; control valve means communicating with the pressure oil in the cylinder means and including means for controlling the extent of opening of a bleed hole to bleed oil out of said cylinder means, said control valve having a valve piston with an annular recess formed thereon, means for connecting the oil from the cylinder means to the valve piston to increase the opening of said bleeding hole by oil pressure from the cylinder means, and a second spring means operating on said valve piston for decreasing the said bleed opening, whereby a given operating condition of the control valve means is established by the balance of both forces to define the extent of opening of the bleeding hole; lever means for rotating manually
  • said oil supply means being a hydraulic pump rotating coaxially with the camshaft of the fuel-injection pump and varying the feed pressure of the oil in response to the rotational speed of the camshaft; said cylinder means being a chamber hydraulically connected with said hydraulic pump; an end cylinder closing one end of said chamber and being movable in response to oil pressure in said chamber, said cylinder being connected to said fuel-argusting rod, the axes 0 being the cylinder and the fuel-adjusting ro substantially parallel to each other, said cylinder arranged to receive both the force of the first spring means and the opposing force of the oil pressure in the chamber, whereby the cylinder is located axially, together with the fuel-adjusting rod, by the balance of the forces of the oil pressure and the said first spring.
  • a governor according to claim 4 wherein only when the rotational speed of the flyweights exceeds a fixed value does said centrifugal force overcome the opposite force of said third spring means to operate said lever arm to operate said control valve means to decrease the opening of said bleeding port.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
US60221A 1969-08-04 1970-08-03 Governor for internal combustion engines of injection type Expired - Lifetime US3640258A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP44061052A JPS4922970B1 (enrdf_load_stackoverflow) 1969-08-04 1969-08-04

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US3640258A true US3640258A (en) 1972-02-08

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US60221A Expired - Lifetime US3640258A (en) 1969-08-04 1970-08-03 Governor for internal combustion engines of injection type

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JP (1) JPS4922970B1 (enrdf_load_stackoverflow)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3916862A (en) * 1973-10-26 1975-11-04 Caterpillar Tractor Co Torque rise limiting device
US3945360A (en) * 1973-10-03 1976-03-23 Robert Bosch Gmbh RPM Regulator for fuel injection pumps
US4052910A (en) * 1976-08-23 1977-10-11 Caterpillar Tractor Co. Governor and decelerator control linkage
FR2368086A1 (fr) * 1976-10-12 1978-05-12 Caterpillar Tractor Co Tringlerie de commande, notamment pour regulateurs de vitesse et autres
US4109629A (en) * 1974-04-01 1978-08-29 C.A.V. Limited Fuel injection pumping apparatus
US4273088A (en) * 1978-02-23 1981-06-16 Robert Bosch Gmbh Apparatus for setting the angular relationship between rotating driving, and driven members
US4291657A (en) * 1978-11-17 1981-09-29 Codrington Ernest R Diesel engine speed governor
WO1981002763A1 (en) * 1980-03-28 1981-10-01 Caterpillar Tractor Co Servo boosted governor control for engines
US4331114A (en) * 1980-10-01 1982-05-25 Caterpillar Tractor Co. Auxiliary engine stoppage apparatus
US4355610A (en) * 1980-03-28 1982-10-26 Caterpillar Tractor Co. Servo boosted governor control for engines
US4453520A (en) * 1980-07-03 1984-06-12 Lucas Industries Limited Liquid fuel pumping apparatus
US4569319A (en) * 1977-02-26 1986-02-11 Daimler-Benz Aktiengesellschaft Air-compressing injection internal combustion engine, especially for passenger motor vehicles
US4884542A (en) * 1987-12-09 1989-12-05 Robert Bosch Gmbh Fuel-injection pump for internal combustion engines, in particular for diesel engines
US20020096141A1 (en) * 2000-11-13 2002-07-25 Bootle Geoffrey D. Governor
US6546853B2 (en) * 2000-06-02 2003-04-15 Sumitomo Wiring Systems, Ltd. Band tightening and cutting device
US20090107451A1 (en) * 2007-10-31 2009-04-30 Caterpillar Inc. Engine speed sensitive oil pressure regulator
US20100163005A1 (en) * 2007-03-16 2010-07-01 Gerhard Meier High-pressure pump for delivering fuel with an improved design of the bearing arrangement for the support of the cam shaft

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2292194A (en) * 1941-05-29 1942-08-04 Gen Motors Corp Engine control means
US2384340A (en) * 1940-05-06 1945-09-04 Reggio Ferdinando Carlo Governing means
US2525653A (en) * 1948-03-26 1950-10-10 Kingseeley Corp Hydraulic speed governor
US3139875A (en) * 1961-08-22 1964-07-07 Cummins Engine Co Inc Fuel supply apparatus for internal combustion engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2384340A (en) * 1940-05-06 1945-09-04 Reggio Ferdinando Carlo Governing means
US2292194A (en) * 1941-05-29 1942-08-04 Gen Motors Corp Engine control means
US2525653A (en) * 1948-03-26 1950-10-10 Kingseeley Corp Hydraulic speed governor
US3139875A (en) * 1961-08-22 1964-07-07 Cummins Engine Co Inc Fuel supply apparatus for internal combustion engine

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3945360A (en) * 1973-10-03 1976-03-23 Robert Bosch Gmbh RPM Regulator for fuel injection pumps
US3916862A (en) * 1973-10-26 1975-11-04 Caterpillar Tractor Co Torque rise limiting device
US4109629A (en) * 1974-04-01 1978-08-29 C.A.V. Limited Fuel injection pumping apparatus
US4052910A (en) * 1976-08-23 1977-10-11 Caterpillar Tractor Co. Governor and decelerator control linkage
FR2363148A1 (fr) * 1976-08-23 1978-03-24 Caterpillar Tractor Co Tringlerie de commande de regulateur et decelerateur
FR2368086A1 (fr) * 1976-10-12 1978-05-12 Caterpillar Tractor Co Tringlerie de commande, notamment pour regulateurs de vitesse et autres
US4569319A (en) * 1977-02-26 1986-02-11 Daimler-Benz Aktiengesellschaft Air-compressing injection internal combustion engine, especially for passenger motor vehicles
US4273088A (en) * 1978-02-23 1981-06-16 Robert Bosch Gmbh Apparatus for setting the angular relationship between rotating driving, and driven members
US4291657A (en) * 1978-11-17 1981-09-29 Codrington Ernest R Diesel engine speed governor
US4355610A (en) * 1980-03-28 1982-10-26 Caterpillar Tractor Co. Servo boosted governor control for engines
WO1981002763A1 (en) * 1980-03-28 1981-10-01 Caterpillar Tractor Co Servo boosted governor control for engines
US4453520A (en) * 1980-07-03 1984-06-12 Lucas Industries Limited Liquid fuel pumping apparatus
US4331114A (en) * 1980-10-01 1982-05-25 Caterpillar Tractor Co. Auxiliary engine stoppage apparatus
US4884542A (en) * 1987-12-09 1989-12-05 Robert Bosch Gmbh Fuel-injection pump for internal combustion engines, in particular for diesel engines
US6546853B2 (en) * 2000-06-02 2003-04-15 Sumitomo Wiring Systems, Ltd. Band tightening and cutting device
US20020096141A1 (en) * 2000-11-13 2002-07-25 Bootle Geoffrey D. Governor
US6807940B2 (en) * 2000-11-13 2004-10-26 Delphi Technologies, Inc. Governor
US20050051132A1 (en) * 2000-11-13 2005-03-10 Delphi Technologies, Inc. Governor
US20100163005A1 (en) * 2007-03-16 2010-07-01 Gerhard Meier High-pressure pump for delivering fuel with an improved design of the bearing arrangement for the support of the cam shaft
US20090107451A1 (en) * 2007-10-31 2009-04-30 Caterpillar Inc. Engine speed sensitive oil pressure regulator
US8511274B2 (en) * 2007-10-31 2013-08-20 Caterpillar Inc. Engine speed sensitive oil pressure regulator

Also Published As

Publication number Publication date
JPS4922970B1 (enrdf_load_stackoverflow) 1974-06-12

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